ENERGY CONSERVATION CYCLE ENGINE

Abstract: An energy conservation cycle engine which can eliminate NOx and unburnt matter, reduces environmental pollution, reduces also a friction loss and vibration of a cycle engine, raises a maximum combustion pressure, reduces CO 2 , reduces the thickness of a main combustion chamber and its weight, reduces a specific weight per output and increases a specific output per weight. A piston has a stepped shape in which a small diameter portion protrudes from a large diameter portion having a cup-like recess, and a cylinder head has a shape for accepting, and fitting to, the piston so as to dispose two combustion chambers. Further, a tapered reduced diameter portion functioning as a fan-shaped nozzle is added so that a combustion gas can efficiently move from the main combustion chamber to a sub-combustion chamber.

Description: TECHNICAL FIELD OF THE INVENTION The present invention relates to a piston reciprocating cycle, which converts a conventional and a special piston reciprocating motions to rotating power. More particularly, the present invention relates to an energy conservation cycle engine in which in order to improve energy conversion efficiency of my previous invention, based on the third law of thermodynamics, "Energy transformation method and its system for piston reciprocating cycle" (Japanese Patent Application No.Hei.7-79292 and U.S. Patent Application Serial No. 08/608,148) by conserving the major portion of the thermal energy within a main combustion chamber, thereby the amount of energy release (a stroke volume of the piston) at the top dead center becomes low and the most of the thermal energy is obtained at after 30 deg. in crank angle . BACKGROUND OF THE INVENTION In the prior arts as shown in Fig.1(a), a combustion chamber is defined by a cylinder head and a piston. The diameter of the combustion chamber of the prior art is comparatively large and a combustion pressure and a combustion temperature are applied to the large area of the combustion chamber and piston. Since cooling is essentially required, as the combustion chamber becomes large-diameter and in a surface area, a cooling loss increases. Moreover, when increasing a maximum combustion pressure, a reinforcement depending on the combustion pressure is required, whereby the weight per output is increased. Similarly, when increasing a maximum combustion pressure, since friction losses of a piston ring or the like are increased, the friction loss per output is increased. In the moment of combustion, usually, a combustion period is extended between nearby 40 deg. to 60 deg. in crank angle after the dead centers. However, when the piston begins to retract from the top dead center, the combustion chamber is communicated with the cylinder, whereby in response to the retraction of the piston, the volume of the combustion chamber is increased rapidly. As a result, an extreme non-constant volume combustion is caused, so that the maximum combustion pressure and the maximum combustion pressure are lowered rapidly, whereby the combustion conditions are deteriorated. Moreover, when setting on the combustion condition reducing NOx, an uncombusted portion of the fuel is increased, and when setting on the combustion condition reducing the uncombusted portion of the fuel, NOx is increased. With reference to a pressure diagram of a constant pressure cycle engine shown in Fig. 2, another description is described. In the conventional constant pressure cycle engine, the major portion of the thermal energy generated by combustion including the thermal energy at the maximum combustion pressure is released as shown in Fig.2, until 30 deg. in crank angle after the top dead center. Since before and after the top dead center, the friction loss is maximized, the thermal energy released is dissipated by the friction force, whereby the amount of work (a stroke volume of the piston) becomes extremely slight. On the one hand, at the best opportunity of 90 deg. in crank angle after the top dead center at which the friction loss is minimized and which is most adapting to release the thermal energy, the thermal energy to be released is reduced to nearby one fourteenth, whereby the thermal energy of nearby 30 percent is lost. In the constant volume cycle engine, since the curves of a pressure diagram shown in Fig.2 further is shifted to the top dead center side, whereby the thermal energy of 30 percent or more is lost. That is, it has been the largest disadvantage in the prior art that the thermal energy to be released is released almost at the time when the friction loss is maximum. The pressure diagram of the constant volume cycle engine shown in Fig.2 is described as compared with the case where we make a bicycle to advance efficiently by stepping down vertically. In the conventional constant pressure cycle engine and the constant volume cycle engine, the major portion of the thermal energy generated by combustion is released until the top dead center to 30 deg. in crank angle after the top dead center. On the other hand, we do not attempt to release the entire energy in the vertical direction at the time when the bicycle pedal is at the top dead center. Especially, at 90 deg. in crank angle after the top dead center where the efficiency of the case of converting an up-and-down motion to rotating power becomes the best timing, the force to be applied to the bicycle pedal is never reduced to nearby one fourteenth. Since we know well the laws of natural from the experimental laws, at the time when the bicycle pedal is at the top dead center, the force to be applied to the bicycle pedal is reduced to the minimum required, and to the timing of 90 deg. in crank angle after the top dead center where the efficiency of the case of converting the up-and-down motion to rotating power becomes the maximum, the force to be applied to the bicycle pedal is expanded increasingly. That is, at the top dead center, the friction loss is maximized, so that the efficiency of the case of converting the up-and-down motion to rotating power becomes lowest. On the one hand, at 90 deg. in crank angle after the top dead center, the friction loss is minimized, so that the efficiency of the case of converting the up-and-down motion to rotating power becomes highest. This practice can be understood readily from Fig.2. Similarly to the case where we make the bicycle to advance efficiently, the system which optimizes the distribution of the amount of releasing with respect to the timing of releasing of the thermal energy is the "Energy transformation method and its system for piston reciprocating cycle" (Japanese Patent Application No.Hei.7-79292 and U.S. Patent Application Serial Number 08/608,148) which this applicant had invented previously. By shifting the timing at which the release of the thermal energy becomes the minimum from the time when the friction loss is maximized to the time when the friction loss is minimized, the system which the "Energy transformation method and its system for piston reciprocating cycle" which increases the efficiency of the case of converting the up-and-down motion to rotating power further is improved is the present invention. Moreover, although this applicant had applied a energy conservation cycle engine that by reciprocating motion of a dual enlarged head piston, a pendulum arm is pendulated to rotate a crankshaft by the pendulating motion to produce rotating power, there has been disadvantages that due to the pendulating motion of the pendulum arm, the volume is increased and the structure is sophisticated, whereby the improvement of the energy conservation cycle engine that a shortened stroke engine is used to rotate the crankshaft directly to convert to rotating power to produce large output in spite of compact and lightweight is provided . The main object of the invention is to improve the various energy conservation cycle engine of the previous application, therefore, it is the object that NOx and the uncombusted portion can be eliminated, thereby environmental pollution being reduced. In converting from a piston motion to rotating power also, they are the objects to provide an increase in a rotating force and to utilize the conserved thermal energy as rotating energy usefully. Furthermore, it is the object that the friction loss and vibration of the cycle engine are reduced to reduce the equivalent to the maximum bearing load, thereby to increase the maximum combustion pressure to reduce CO 2 . Moreover, as further object, thinning in wall and reduction in weight of a main combustion chamber, weight reduction of a specific weight per output and an improvement of a scavenging effect are provided. Furthermore, it is the object that, without reference to a kind of fuel, a fuel ignition system, the number of cycles, a scavenging system and a type of the engines, while a specific output per weight is increased, the friction loss is reduced, thereby reducing environmental pollution including CO 2 . DISCLOSURE OF THE INVENTION To solve the problems of the prior arts an engine according to claim 1 is provided wherein a shape of a piston is formed as indicated in Fig.1(c) into a stepped shape, comprising an large diameter portion (hereinafter referred to as an enlarged head piston) having a cup-like recess, and a small diameter second piston (hereinafter referred to as a small piston) which is protruded from the cup-like recess. A cylinder head has a shape for accepting said pistons to fit, consequently, a first combustion chamber (hereinafter referred to as a main combustion chamber) is defined by the small piston 23 and the cylinder head and a second combustion chamber (hereinafter referred to as a sub-combustion chamber) mainly defined by the enlarged head piston 22 and the cylinder head. For example, we consider a small piston having a diameter of one fifth of the enlarged head piston. Since the small piston is the diameter of one fifth of the enlarged head piston, the diameter of the main combustion chamber is also one fifth of that of the sub combustion chamber. Therefore, the thickness of the cylinder head defining the main combustion chamber can be reduced to one fifth, thereby the weight of the cylinder is reduced. Moreover, since the area of the piston defining the main combustion chamber is reduced to one twenty-fifth, the minimum bearing load applied to the piston is reduced to one twenty-fifth if the same combustion pressure is applied. Therefore, the maximum combustion pressure can be increased and the friction loss can be decreased. If the main combustion chamber and the sub combustion chamber is communicated at an angle of 40 deg. in crank angle after the top dead center, the stroke volume of the piston is concluded with 1/5 as compared with the conventional one, whereby the amount of the energy released becomes 1/25, and consequently 24/25 of the energy which used to be released is conserved. By releasing the conserved energy when the efficiency of the case of converting the linear motion to rotating power becomes the best timing, an energy conversion efficiency of the entire engine is increased. If the volume of the combustion chamber exceeds a certain volume, the combustion temperature exceeds 3500 °C and the combustion pressure increases, it is preferable to add a water injection means 5 to increase a volume of water vapor. Moreover, an adiabatic non-cooling engine which is most likely to adapt to the hydrogen fuel can be realized, thereby by the steam and internal combustion coalition engine, an environmental pollution will be decreased. The pressure difference between the two combustion chambers at the time of communication, a combustion gas is injected into the cup-like recess 1 to be whirled, the fuel is burnt perfectly, thereby CO 2 and the environmental pollution are reduced. To increase the efficiency of the engine, it is preferable to provide a tapered reduced diameter portion 7 acting as a fan-shaped nozzle to the cylinder head. The combustion gas can move from the main combustion chamber to the sub-combustion chamber quickly. Moreover, as shown in Fig.1 (d), at least a part of the cup-like recess of the enlarged head piston consists of a straight line, and a scavenging port and an exhaust port are disposed at the side of the cylinder, thereby the scavenging effect may be improved. BRIEF DESCRIPTION OF THE DRAWINGS Fig.1 (a), (b), (c) and (d) are partial sectional views for describing, as compared with the prior art, an embodiment of an energy conservation cycle engine of type A of the present invention. Fig.2 is a schematic chart showing the changes of the combustion pressure with respect to a crank angle of the energy conservation cycle engines of various types according to the invention. Fig. 3 is a partially sectional view of an embodiment of an energy conservation cycle engine of type D according to the invention. Fig. 4 is a partially sectional view showing a plane of the embodiment of an energy conservation cycle engine of type D of Fig.3. Fig. 5 is a partially sectional view of an embodiment of an energy conservation cycle engine of type B according to the invention. Fig. 6 is a partially sectional view showing a plane of the embodiment of the energy conservation cycle engine of type B of Fig.3. Fig. 7 is a partially sectional view of an embodiment of an energy conservation cycle engine of type E according to the invention. Fig. 8 is a partially sectional view of an embodiment of an energy conservation cycle engine of type C according to the invention. Fig. 9 is a partially sectional view of an embodiment of an energy conservation cycle engine of type F according to the invention. Fig. 10 is a partially sectional view of an embodiment of an energy conservation cycle engine of type G according to the invention. Fig. 11 is a partially sectional views for comparing and describing an utilization method of a crankshaft, including the crankshaft and an engagement synchronous means of the energy conservation cycle engines of various type according to the invention. Fig. 12 is a sectional view for describing a crankshaft-mounting situation of the energy conservation cycle engines of type D, type E, type F and type G along line A-A in Fig. 4 Fig. 13 is a general constitution view showing an embodiment of the energy conservation cycle engines of various types according to the invention. Fig. 14 is a general constitution view showing another embodiment of the energy conservation cycle engines of various types according to the invention. Fig. 15 is a general constitution view showing a further embodiment of the energy conservation cycle engines of various types according to the invention. Fig. 16 is a general constitution view showing a yet further embodiment of the energy conservation cycle engines of various types according to the invention. DESCRIPTION OF THE SYMBOLS 1: cup-like recess 2: tapered root section 3: check valve 4: one-way air channel 5: fuel and water injection means 6: sword guard projections and depressions 7: tapered reduced diameter portion 8: pendulum hole 9: piston side cam 10: semicircular track 11: the pendulum side cam 12: parallel track 13: body side cam 14: inclined air passage 15: noise-reducing groove (a plurality of grooves extending oblquely ) 16: cylinder bore 17: engagement synchronous means 18: exhaust-section heat exchanger means 19: reduced diameter section heat exchanger member 20: combustion section heat exchanger member 21: heat resisting and corrosion resisting heat-insulating member 22: enlarged head piston 23: small piston ( second piston ) 24: combustion chamber with the expanded diameter ( second combustion chamber ) 25: combustion chamber with the reduced diameter ( first combustion chamber ) 26: pendulum arm 27: crankshaft 28: flywheel 29: crankshaft side translation bearing 30: dual enlarged head piston 31: cylinder 32: cylinder head 33: exhaust port 34: scavenging port 35: toothed wheel 36: exhaust section 37: turbo charger 38: piston bore 39: pendulum side cam 40: crankshaft side cam 41: heat-insulating materials 42: water injection means 43: projection 44: supercharging piston 45: charging valve 46: scavenging valve 47: the bearing unit 48: pendulum side parallel track 49: tapered periphery section 50: inclined scavenging port 52: cylinder-side parallel track assembling hole 53: pendulum side translation bearing 54: connecting rod 55: piston-supercharger 56: mechanical supercharger 57: controller 58: dovetail groove for assembling E: isolation releasing W: water A: air O: exhaust a: best opportunity b : worst period C: crankshaft angle P: combustion pressure M: motoring H: heat-generating ratio S: isolation initiation E: isolation release BEST MODE OF THE INVENTION With reference to an embodiment of an energy conservation cycle engine (the energy conservation cycle engine of type A) using a conventional crank mechanism of Fig.1 (b), (c) and (d) and Fig.1, the invention is described. From the nearby central portion of a cup-like recess 1 of an enlarged head piston 22, a small piston 23 having a tapered root section 2 (including a cylindrical shape) is protruded. The enlarged head piston reciprocates between the top dead center and the bottom dead center, and in the energy conservation cycle engine of a two-stroke cycle of type A performing conventional scavenging and exhaust, as lifting of the enlarged head piston 22, by means of the small piston 23 having a tapered root section 2, the isolation of the main combustion chamber 25 with the reduced diameter having the tapered reduced diameter portion 7 is initiated. Subsequently, the air compressed by the main combustion chamber 24 with the expanded diameter is injected into the main combustion chamber 25 with the reduced diameter through the one-way air channel 4 including a check valve 3 and an inclined air passage 14 and an inclined air passage 14. After the compressed air in the main combustion chamber with the reduced diameter is mixed and churned with the fuel injected from a fuel and water injection means 5, the air is ignited to combust. In the main combustion chamber 25 with the reduced diameter exceeding a certain volume, water injecting can be performed, whereby the steam and internal combustion coalition engine can be realized. When the enlarged head piston 22 begins to retract, the pressure in the combustion chamber with the expanded diameter begins to reduce, and by means of sword guard-like projections and depressions 6 provided on a periphery of the small piston 23 in a multi-stage form, a leak of the combustion gas can be optimized. When the enlarged head piston 22 retracts, for example, up to 40 deg. in crank angle after the dead centers, the main combustion chamber 25 with the reduced diameter is communicated with the main combustion chamber 24 with the expanded diameter. At this time, the tapered reduced diameter portion 7 functions as the fan-shaped nozzle, whereby the combustion gas is injected into the cup-like recess 1 at high speed, so that the combustion gas is churned by difference in pressure, thereby the uncombusted portion being combusted perfectly. Moreover, by a reaction plus an impulse and plus a pressure due to speed-type energy and volume-type energy, the enlarged head piston can be retracted strongly to generate a rotating force to improve thermal efficiency and to reduce environmental pollution. Moreover, when the enlarged head piston shown in Fig. 1 (d) retracts, for example, up to 40 deg. in crank angle after the dead centers, the isolation combustion in the main combustion chamber 25 with the reduced diameter is released, whereby the tapered reduced diameter portion 7 constitutes the fan-shaped nozzle to inject the combustion gas onto the top of the small piston correctly and at high speed. However, the deeper the recess 1 is, the more the oscillation of the piston is reduced, so that a scavenging efficiency is lowered, whereby on a part of the recess 1, a straight line portion 49 (hereinafter referred to as a tapered periphery section) is provided and to provide an inclined scavenging port 34 being fitted to the taper angle as required to inject a scavenging gas onto a bottom of the recess 1 to improve the scavenging efficiency. Moreover, by addition of dynamic pressure, in a process providing a great increase in output, a high speed injecting and churning combustion based on a great difference in pressure can be realized to eliminate the uncombusted portion two times completely to generate a great rotating power to greatly increase the thermal efficiency and to greatly reduce environmental pollution to shift to the conventional scavenging and exhaust through the inclined scavenging port 34 and a inclined exhaust port 33. Fig. 3 shows a dual enlarged head piston 30 having enlarged head pistons 22 at both right and left sides. Moreover, the small pistons 23 has a tapered end sections 2, a inclined noise reducing grooves 15 at its top and projections and depressions 6 therebetween which protrudes from the center of the cup-like recess 1 of the enlarged head pistons 22 of the right and left of the dual enlarged head piston 30. Said dual enlarged head piston 30 reciprocates between the top dead center and the bottom dead center to perform the conventional exhaust and scavenging. In a two-cycle energy conservation cycle engine of type D using such as dual enlarged head piston 30, at a compression stroke process after scavenging, by the small piston 23, the isolation of the main combustion chamber 25 with the reduced diameter is initiated. Subsequently, the air compressed in the combustion chamber 24 with the reduced diameter is injected into the main combustion chambers 25 with the reduced diameter through the one-way air channels 4 including the check valves 3 and the inclined air passages 14. After the compressed air in the main combustion chamber 25 with the reduced diameter is churned and mixed up with the fuel injected from the fuel and water injection means 5 and is ignited to combust. Since in the main combustion chamber 25 with the reduced diameter, scavenging is difficult, residual gases are increased. As a result, at combusting, NOx is hard to generate. Moreover, in the main combustion chamber 25 with the reduced diameter exceeding a certain volume, water injecting further is performed, whereby the steam and internal combustion coalition engine can be realized. According to the steam and internal combustion coalition engine, the combustion which NOx and the uncombusted portion are not caused can be performed. When the enlarged head piston 22 begins to retract, the pressure in the small piston 23 begins to reduce, and by means of sword guard-like projections and depressions 6 provided on the periphery of the small piston 23 in the multi-stage form, the leak of the combustion gas can be optimized. When the enlarged head piston 22 further retracts, the main combustion chamber 25 with the reduced diameter is communicated with the main combustion chamber 24 with the expanded diameter. While the noise-reducing groove 15 of the small piston 23 establishes the injecting direction of the combustion gas, the sounds is reduced. Subsequently, 7 constituting the fan-shaped nozzle, the tapered reduced diameter portion injects the combustion gas to the cup-like recess 1, whereby a rotating force is increased. At this time, while the combustion gas is churned by difference in pressure at high speed, the combustion gas is designed to be combusted, whereby the uncombusted portion can be eliminated completely two times. The enlarged head piston 22 can be retracted strongly by the speed-type energy plus volume-type energy. At this point, a reciprocating motion by a pendulum piston crank mechanism in the energy conservation cycle engine of type B is described. The most important practice is that the reciprocating motion can not decrease rotating power. In a perfectly elastic collision, since in the moment of the collision, the kinetic energy is not decreased, the reciprocating motion of the two-cycle dual enlarged head piston becomes the most preferable manner. Moreover, it is important that at converting the reciprocating motion to rotating motion, the kinetic energy also is not decreased, from this reason, the reciprocating motion by the pendulum piston crank mechanism becomes preferable. That is, the reciprocating motion of the pendulum can be continued at a constant speed, even though a weight is increased regardless of the weight, as far as the length is identical. When a conventional one cylinder crank engine is rotated with full force, the rotation is performed eight times to ten times by inertia, in contrast with this, when being rotated as a substitute of the reciprocating portions such as the piston under the condition of hanging a weight of 5 kg with full force, due to a great decrease in the kinetic energy it becomes hard to rotate even only one time. Therefore, the two-cycle pendulum piston crank mechanism becomes the preferable manner. Whereas the decrease and loss of the kinetic energy are 30 percentage to 20 percentage in the conventional four-cycle engine and 15 percentage to 10 percentage in the conventional two-cycle engine, it approaches zero percentage in the two-cycle dual pendulum piston engine. Moreover, in the conventional crank engine, the weight reduction of the reciprocating portions provides large effect on a specific output such as the increase in the piston speed and the improvement in the thermal efficiency. The pendulum arm swings to rotate the crankshaft to produce power, the volume is increased and the structure is sophisticated. In order to convert kinetic energy to rotating power efficiently, it is preferable to realize a shortened stroke, from this reason, when by reciprocating motion of the dual enlarged head piston, the crankshaft is rotated directly to convert to rotating power, the large output in a form of the compact and lightweight further can be produced. Accordingly, when on the nearby central portion of the cylindrical portion of the dual enlarged head piston, providing a parallel track accepting and retaining a crankshaft side cam or a crankshaft side translation bearing (including a slide way) in a manner to reciprocally move freely in parallel with and in radius direction, and accepting and retaining in a manner to reciprocally move freely the crankshaft side cam or the crankshaft side translation bearing bearing the crankshaft rotatably freely, by the reciprocating motion of the dual enlarged head piston, the crankshaft including an engagement synchronous means 17 and a flywheel can be rotated directly to produce rotating power efficiently, and a specific volume and a specific weight can be greatly reduced. Hereinafter, this mechanism is described specifically. An embodiment of an energy conservation cycle internal combustion engine of type D shown in Fig. 3, Fig.4 and Fig.12 is described. In the dual enlarged head piston, a part of the cup-like recess of the piston is formed into a linear form, further, in the cylinders of the right and left, the inclined scavenging ports 50 and the inclined exhaust ports 51 performing scavenging and exhaust are provided. Moreover, by a reaction plus an impulse and plus a pressure due to the speed-type energy plus the volume-type energy, the enlarged head piston can be retracted strongly to generate a great rotating force to improve thermal efficiency and to reduce environmental pollution to shift to the conventional scavenging and exhaust. Moreover, the inclined scavenging ports 50 are slanted in a manner to fit to a taper angle of a tapered periphery section to inject a scavenging gas onto the bottoms of the recesses 1 and the inclined exhaust ports 51 are slanted mainly in the reversing direction thereto to improve the scavenging efficiency. Hereinafter, a mechanism according to this embodiment is described specifically. Before and after the dead centers of the right and left, the conventional scavenging and exhaust are performed through the inclined scavenging ports 50 and the inclined exhaust ports 51. In the compression process after scavenging, by the tapered root sections 2, the sword guard projections and depressions 6 and the small pistons provided with a plurality of noise reducing grooves 15 extending parallel or inclinedly with respect to the moving direction in a manner to remain the rear ends as required on the periphery of the projections wide in width of the tips, the isolation of the main combustion chambers 25 with the reduced diameter having the tapered reduced diameter portions 7 is initiated. Subsequently, the air compressed in the main combustion chamber 24 with the expanded diameter is injected from a plurality of inclined air passages 14 through the one-way air channels 4 including the check valves 3 inserted from the combustion chamber with the expanded diameter sides and fixed into the inside of the main combustion chamber with the reduced diameter in a slanting direction and to be churned and mixed up with the fuel injected from the fuel injection devices 5 to approach extremely in the main combustion chamber with the reduced diameter to combust under the isolated condition. In the main combustion chambers 25 with the reduced diameter exceeding a certain volume, water injecting by a water injection means 42 further can be performed, whereby the steam and internal combustion coalition engine can be realized. When the dual enlarged head piston begins to retract, the pressure in the combustion chamber with the expanded diameter begins to reduce, whereby by means of sword guard-like projections and depressions 6 provided on a periphery of the small piston in a multi-stage form, the pressure is reduced in multistages to establishes a leak of the combustion gas optimally. When the enlarged head piston further retracts, the isolation combustion in the main combustion chambers with the reduced diameter is released, and while first, by the noise reducing grooves 15 of the small pistons, the injecting direction of the combustion gas is established, the noise is reduced, while secondly, the tapered reduced diameter portions 7 constitutes the fan-shaped nozzles to inject a combustion gas onto the recesses 1 correctly and at high speed to greatly increase a rotating force, in a high speed injecting process a high-speed injection and a churn combustion by the large difference in pressure is realized, whereby the uncombusted portion is eliminated completely. In parallel with this, by a reaction plus an impulse and plus a pressure due to the speed-type mass energy plus the volume-type energy, the enlarged head piston is retracted strongly to generate a great rotating force to improve thermal efficiency and to greatly reduce environmental pollution. And then, it shifts to the conventional scavenging and exhaust, and the inclined scavenging ports 50 are slanted in a manner to fit to a taper angle of a tapered periphery sections 49 to inject a scavenging gas onto the bottoms of the recesses 1 and the inclined exhaust ports 51 are slanted mainly in the reversing direction thereto to improve the scavenging efficiency. Describing another description with reference to Fig. 3 and Fig. 4, on a little to center of the right and left of the cylindrical cylinder, the inclined scavenging ports 50 and the inclined exhaust ports 51 are provided respectively as required, and between the cylinder heads fixed to the right and left and the respective enlarged head piston of the dual enlarged head piston, the combustion chamber with the expanded diameter is defined. In the approximate center of the cylinder head, the combustion chambers with the reduced diameter are provided respectively, and such that the fuel can be injected and combusted, the fuel injection devices 5 are provided respectively, further, the water injection means 42 for modifying the combustion to a combustion greatly reducing NOx are additionally provided respectively. Moreover, in order to eliminate the cooling loss from the main combustion chambers with the reduced diameter and the combustion chambers with the expanded diameter, the combustion chambers with the reduced diameter, the tapered reduced diameter portions 7, the projections 43, said small piston, the tapered root sections 2 and the recesses 1 are provided as a heat resistance, corrosion resistance and heat insulation structure by a heat resisting and corrosion resisting materials 21 and a heat insulating materials 41. Moreover, on the heat resisting and corrosion resisting materials 21 of the combustion chambers with the reduced diameter, a plurality of inclined air passages 14 are provided. Moreover, as is mentioned above, since for the energy conservation cycle engine, the shortened stroke engine or a very-shortened stroke engine is preferable, on an nearby central position and in the radius direction of the cylinder, and into a cross-like form, the cylinder bore 16 and a cylinder-side parallel track assembling ports 52 are provided, and on an nearby central position and in the radius direction of the dual enlarged head piston, and into a cross-like form, the piston bore 38 and the cylinder-side parallel track assembling ports 52 are provided. A parallel track 12 for rotating the crankshaft born by a bearing unit 47 through the reciprocating motion is provided in parallel, and to insert and retain a crankshaft side cam 40 or a crankshaft side translation bearing 29 which is rotatably outer-fitted and pivoted to the crankshaft between the parallel track 12 in a manner to reciprocally move freely and to rotate directly the crankshaft including the flywheel by the reciprocating motion of the dual enlarged head piston to produce rotating power. With reference to Fig.5 and Fig.6, another embodiment of the energy conservation cycle internal combustion engine of type B is described. Since a primary section of the energy conservation cycle engine of type B is similarly to said energy conservation cycle engine of type D shown in Fig.3, the pendulum piston crank mechanism and a portion which is lacking in the description are described. The pendulum arm reciprocates in the right and left directions in a manner to facilitate the pendulating motion between the left dead center and the right dead center of the cylinder provided with the cylinder bore 16. In the nearby central portion of the cylindrical portion of the dual enlarged head piston, the piston bore 38 which the pendulum arm is inserted is provided, and in radius direction, a pendulum side cam 39 or a pendulum side translation bearing 53 is inserted and retained. Providing the parallel track 12, the translation bearing 53 is inserted and retained in a manner to reciprocally move freely therein. By reciprocating motion of the dual enlarged head piston, the pendulum arm oscillates, and between the parallel track 12, the pendulum side cam 39 or the pendulum side translation bearing 53 moves in a manner to reciprocate readily. The pendulum arm hanging the upper thereof by a body side 13 in a manner to facilitate the pendulating motion rotates the crankshaft and the flywheel by oscillation of the pendulum arm. By the crankshaft side translation bearing 29 (including the slide way) or the crankshaft side cam 40 pivoted by the pendulum arm in a manner to facilitate the up-and-down motion into the pendulum side parallel track 48, the crankshaft is pivoted rotatably freely. According to this constitution, by the reciprocating motion of the dual enlarged head piston, the pendulum arm is pendulated to rotate the crankshaft by the pendulating motion to produce rotating power. When the bore of the combustion chamber with the reduced diameter is reduced, for example, to one fifth in the diameter to realize the isolation combustion, a wall thickness of the high pressure main combustion chambers with the reduced diameter can be reduced up to one fifth to achieve great weight reduction, whereby the churn combustion which is approached to the constant volume combustion of twenty-five times as compared with the prior art is realized. Moreover, since, due to the high-speed injection and churn combustion by the large difference in pressure caused at the isolation combustion, for the combustion period of one time, the combustion condition can be improved two times to the limit, the combustion can be greatly improved. Moreover, since, including the adiabatic non-cooling engine also by the steam and internal combustion coalition engine water-injecting from the water injection means 42 , NOx and the uncombusted portion are eliminated completely at same time, the improvement of two times for the combustion of one time can be performed, in addition, the load causing the maximum friction load and the maximum bearing load due to the maximum combustion pressure can be reduced to one twenty-fifth to greatly reduce vibration factors. On the one hand, while the speed-type mass energy and volume-type energy are injected into the recesses 1, said energy being included in the high pressure gas including the water vapor mass volume increased greatly, and to retract the dual enlarged head piston strongly by a reaction plus an impulse and plus a pressure due to the speed-type energy and volume-type energy and to generate a large rotating force, the influences of preignition and an abnormal combustion also are reduced to one twenty-fifth, whereby an early perfect-combustion completion technology using the preignition and the abnormal combustion effectively can be realized. Moreover, the combustion chambers with the expanded diameter become the thin-walled combustion chamber low in pressure and low in temperature by a large amount, whereby, while the entire engine is greatly reduced in weight to greatly increase a specific output per unit weight, environmental pollution including NOx can be greatly reduced. An embodiment of an energy conservation cycle internal combustion engine of type E shown in Fig.7 is described. The basic part of the energy conservation cycle engine is similar to the engine, which has been already explained above. In this embodiment, by the engagement synchronous means 17 coupled oppositely, the opposite reciprocating motions of the respective dual enlarged head piston in the embodiment of an energy conservation cycle internal combustion engine of type D are synchronized to greatly reduce vibration, thereby a very-large-scale energy conservation cycle internal combustion engine of type E being able to be realized. That is, from the nearby central portions of the recesses 1 having tapered periphery sections 49 of the enlarged head pistons of the right and left sides of the respective dual enlarged head piston provided oppositely, the small pistons having the tapered root sections 2 are protruded, whereby the dual enlarged head pistons are facilitated to perform the opposite reciprocating motion between outer dead centers and inner dead centers. Before and after the respective outer dead center and before and after the respective inner dead center, the conventional scavenging and exhaust are performed through the inclined scavenging ports 50 and the inclined exhaust ports 51 respectively. In the compression process after scavenging, by the tapered root section 2, the sword guard projections and depressions 6 and the small pistons provided with a plurality of noise reducing grooves 15 extending parallel or inclinedly with respect to the moving direction in a manner to remain the rear ends as required on the peripheries of the projections wide in width of the tips, the isolations of the main combustion chambers 25 with the reduced diameter having the tapered reduced diameter portions 7 respectively are initiated, subsequently, the air compressed in the main combustion chambers with the expanded diameter are injected respectively from a plurality of inclined air passages 14 through the one-way air channels 4 including the respective check valves 3 inserted and fixed from the combustion chambers with the expanded diameter side in a slanting direction in the respective main combustion chambers with the reduced diameter and to be churned and mixed up with the fuel injected from the respective fuel injection devices 5 to realize a constant volume extreme approach isolation combustion in the respective main combustion chamber with the reduced diameter. In the main combustion chambers 25 with the reduced diameter exceeding a certain volume, water injecting by the water injection means 42 further can be performed, whereby the steam and internal combustion coalition engines can be realized. When the respective dual enlarged head piston begins to retract, the pressure in the respective combustion chambers with the expanded diameter begin to reduce, whereby by means of the sword guard-like projections and depressions 6 provided on the peripheries of the small pistons in a multi-stage form, the pressure is reduced in multistage to establishes a leak of the combustion gas optimally. When the enlarged head pistons further retract respectively, the isolation combustion in the main combustion chamber with the reduced diameter are released, and while first, by the noise reducing grooves 15 of the respective small pistons, the injecting direction of the combustion gas is established, the sounds is reduced, while secondly, the respective tapered reduced diameter portions 7 constitute the fan-shaped nozzles to inject a combustion gas onto the recesses 1 correctly and at high speed to greatly increase the rotating force, in a high speed injecting process a high-speed injection and churn combustion by the large difference in pressure is realized, whereby the uncombusted portion is eliminated completely. Furthermore, by a reaction plus an impulse and plus a pressure due to the speed-type mass energy and the volume-type energy, the respective enlarged head piston is retracted strongly to generate the great rotating force to improve thermal efficiency and to greatly reduce environmental pollution, and to shift to the respective conventional scavenging and exhaust. The inclined scavenging ports 50 are slanted in a manner to fit to a taper angle of a tapered periphery sections 49 to inject a scavenging gas onto the bottoms of the recesses 1 and the inclined exhaust ports 51 are slanted mainly in the reversing direction thereto to improve the scavenging efficiency. In the energy conservation cycle engine of type E shown in Fig.7, by the synchronous means 17, the opposite reciprocating motions of the dual enlarged head pistons are synchronized to reduce vibration greatly, whereby a very-large-scale energy conservation cycle internal combustion engine of type E can be realized. Inclined scavenging ports 50 and the inclined exhaust ports 51 are provided at each cylinder respectively, and the combustion chamber with the expanded diameters are defined by the cylinder heads and the enlarged head pistons. Furthermore, in the approximate centers of the cylinder heads, the main combustion chambers with the reduced diameter having the tapered reduced diameter portions 7 are defined, and such that the fuel can be injected and combusted, the fuel injection devices 5 are provided respectively. Moreover, the water injection means 42 for modifying the combustion to a combustion reducing NOx greatly are additionally provided respectively, and various members are provided as the heat resistance, corrosion resistance and heat insulation structure. Moreover, since as is mentioned above, for the energy conservation cycle engine, the shortened stroke engine or a very-shortened stroke engine is preferable, in the case of realizing compression ignition engine, in order to reduce a useless volume, said heat resisting and corrosion resisting materials 21 may be the materials which elasticity is combined as required. On an nearby central position of the respective dual enlarged head piston and in the radious direction, the parallel tracks 12 for rotating the crankshaft by the reciprocating motion are provided in parallel respectively to insert and retain the crankshaft side cams 40 or the respective crankshaft side translation bearings 29 which are rotatably freely outer-fitted and pivoted to the crankshaft between the respective parallel tracks 12 in a manner to reciprocally move freely respectively. The respective crankshaft including the engagement synchronous means 17 by the opposite reciprocating motions of the respective dual enlarged head piston is directly rotated to produce rotating power. With reference to Fig.8, an embodiment of the energy conservation cycle internal combustion engine of type C is described. Since a primary section of the energy conservation cycle engine of type C is similarly to said energy conservation cycle engine of type E shown in Fig.7, the opposed pendulum piston crank mechanism is described. In the energy conservation cycle engine of type C, said energy conservation cycle engines of type B shown in Fig. 5 and Fig. 6 are combined respectively oppositely, by the respective pendulum arm, the crankshafts and the engagement synchronous means 17, the opposite reciprocating motion of the dual enlarged head pistons is synchronized to greatly reduce vibration, whereby a very-large-scale energy conservation cycle engine of type E can be realized. Although when a top-surface shape of the dual enlarged head piston is formed into a deep recess, the combustion gas injected at high speed from the tapered reduced diameter portion 7 can be facilitated to be trapped to reduce a heat load, the scavenging effect is deteriorated, whereby, in the case that the scavenging effect is taken seriously, other than forming the periphery into a tapered shape the recess may be formed the recess into a shallow shape increasingly to make it a plane shape. In response thereto, a projection 43 also being accepted is formed into the plane shape. When the combustion chambers with the reduced diameter are reduced to one fifth to realize the isolation combustion, the maximum bearing load due to the maximum combustion pressure can be reduced to one twenty-fifth, whereby the maximum bearing load also is greatly reduced up to a maximum compression pressure, so that NOx caused by a great increase in the maximum combustion pressure by which the maximum compression pressure is greatly increased also can be reduced. By the reciprocating motion of the two-cycle dual pendulum piston which the decrease and loss of the kinetic energy are very insignificant, the crankshaft including the engagement synchronous means 17 through the pendulum arm is rotated to produce rotating power. With reference to Fig.9, an embodiment of the energy conservation cycle internal combustion engine of type F is described. The respective inside of the dual enlarged head pistons is provided as supercharging piston 44. On a little to center of the right and left of the respectively cylindrical cylinder provided oppositely, the inclined scavenging ports 50 and the inclined exhaust ports 51 defining the inclined injection ports respectively are provided inclinedly in the opposite direction each other. between the cylinder heads fixed to the right and left and the respective enlarged head piston of the dual enlarged head pistons, the combustion chambers with the expanded diameter are provided and the respective inside of the dual enlarged head pistons is provided as the supercharging pistons 44. Moreover, between the supercharging pistons 44, the piston superchargers are defined ; on the approximate centers of the cylinder heads, the combustion chamber with the reduced diameter are provided respectively ; such that the fuel can be injected and combusted, the fuel injection devices 5 are provided respectively ; and the water injection means 42 for combusting and reducing greatly NOx caused by the combustion further are additionally provided respectively. In order to eliminate the cooling loss from the main combustion chamber with the reduced diameter and the combustion chamber with the expanded diameter, by a heat resisting and corrosion resisting materials 21 and a heat insulating materials 41, each member as described above is provided as a heat resistance, corrosion resistance and heat insulation structure, and on the peripheries of the recesses 1, the tapered periphery sections 49 fitted to the slant of the inclined scavenging ports 50 improving the scavenging efficiency are provided. Moreover, since as is mentioned above, for the energy conservation cycle engine, the shortened stroke engine or a very-shortened stroke engine is preferable, on the central portion, a piston supercharger which makes the improvement of a compression ratio possible by a very high supercharging is provided and moreover, the piston supercharger is designed to be constituted by the supercharging piston 44 and, a charging valve 45 and a feed valve 46, whereby the charging valve 45 is communicated with the turbo charger side and the feed valve 46 is communicated with the inclined scavenging port 50, thereby the improvement of the compression ratio being able to be greatly improved. On the nearby central positions of the respective dual enlarged head piston and in the radious direction, the parallel tracks 12 for rotating the crankshafts by the opposite reciprocating motion are provided in parallel respectively to insert and retain the crankshaft side cams 40 or the respective crankshaft side translation bearing (including a slide way) 29 which is rotatably outer-fitted and pivoted to the crankshaft between the respective parallel track 12 in a manner to reciprocally move freely respectively, and the respective crankshaft including the engagement synchronous means 17 is rotated directly by the opposite reciprocating motion of the dual enlarged head pistons to produce rotating power. An embodiment of the energy conservation cycle internal combustion engine of type G shown in Fig.10 is described. A two-cycle energy conservation cycle engine of type G is a very-large-scale energy conservation cycle internal combustion engine in which a variable compression ratio is made improvable by coupling the respective cylinder oppositely by the inner cylinder ; and synchronizing the opposite reciprocating motions of the respective dual enlarged head piston by the engagement synchronous means 17 to greatly reduce vibration. And then, a great rotating force is generated to improve thermal efficiency and to greatly reduce environmental pollution and to shift to the respective conventional scavenging and exhaust, and the inclined scavenging ports 50 are slanted in a manner to fit to a taper angle of the tapered periphery sections 49 to inject the scavenging gas onto the bottoms of the recesses 1. At this time, the inclined exhaust ports 51 can be designed to be slanted mainly in the reversing direction thereto to improve the scavenging efficiency. Specifically, on the right and left sides of the respective cylinder provided oppositely, the cylinder heads are fixed respectively to be coupled oppositely, and on a little to center of the right and left of the respective cylinder, the tapered periphery sections fitted to the slant of the inclined scavenging ports 50 improving the scavenging efficiency are provided, and the inclined scavenging ports 50 injecting the scavenging gas onto the bottoms of the recesses 1 and the inclined exhaust port 51 being slanted in the reversing direction thereto are provided. On the inside between the cylinder heads fixed to the right and left respectively and the dual enlarged head piston, the combustion chambers with the expanded diameter are defined, and on the outside therebetween, the piston supercharger are defined respectively, and on an approximate center of the respective inner cylinder head, the combustion chambers with the reduced diameter are defined respectively and are communicated. And then, providing the charging valve 45 including a lead valve and the feed valve 46 on the respective outer cylinder head, the air is supplied from the turbo charger side to the piston, and in order to feed the air, during feeding air, the charging valve 45 and the inclined scavenging port 50 are communicated with the feed valve 46, on the respective combustion chambers with the reduced diameter, the fuel injection devices 5 are provided, and the water injection means 42 for improving this combustion to the combustion which NOx is reduced greatly are provided and in order to eliminate the cooling loss from the main combustion chamber with the reduced diameter and the combustion chamber with the expanded diameter, each member further is provided as a heat resistance, corrosion resistance and heat insulation structure by a heat resisting and corrosion resisting materials 21 and a heat insulating materials 41. Although, as is mentioned above, for the energy conservation cycle engine, the shortened stroke engine or a very-shortened stroke engine is preferable, in the case of the very-shortened stroke engine, the great improvement of the compression ratio is hard, whereby by said piston supercharger, the very high supercharging including the turbo charger can be realized. On nearby central positions of the outsides of the respective dual enlarged head piston and in the radious direction, the parallel tracks 12 for rotating the crankshaft by the reciprocating motion are provided in parallel respectively. Moreover, the crankshaft side cams 40 or the respective crankshaft side translation bearings 29 which is rotatably outer-fitted and pivoted to the crankshaft are inserted and retained between the respective parallel track 12 in a manner to reciprocally move freely respectively, and by the opposite reciprocating motion of the respective dual enlarged head piston, the respective crankshaft including the engagement synchronous means 17 is directly rotated to produce rotating power. With reference to Fig.11, an use example of a crankshaft is described. In an energy conservation cycle engine of type A, since in accordance with the conventional manner, to one crankshaft, 27 the cylinder is coupled by one cylinder, a three-cylinders engine can be realized. In the case of energy conservation cycle engines of type B and type D, since to a piece of crankshaft, the cylinders is coupled by two cylinders in increment of two cylinders such as two cylinders, four cylinders, six cylinders and eight cylinders, the multiplication in cylinder can be realized. In the case of energy conservation cycle engines of type C, type E, type F and type G, two pieces of the crankshaft are required, and since in type C and type E of these systems, the cylinders are coupled by four cylinders, in increment of four cylinders such as four cylinders, eight cylinders and twelve cylinders, the multiplication in cylinder can be realized. Moreover, in the case of energy conservation cycle engines of type F and type G, since the cylinders are coupled by two cylinders, with coupling by two cylinders in increment of two cylinders such as two cylinders, four cylinders, the multiplication in cylinder can be realized. Moreover, although due to the system having the crankshaft of two pieces, a synchronous means such as the engagement synchronous means using a toothed wheel 35 is required and the vibration can be greatly reduced, thereby to be adapted to the increase in output of the engine With reference to Fig.12, a mounting method of crankshafts of the energy conservation cycle engines of type D, type E, type F and type G is described. On the nearby central position and in the radious direction, and in the axial direction of the cylinder and into a cross-like form, the cylinder bore 16 and a cylinder-side parallel track assembling port 52 are provided, further, on the nearby central position and in the radious direction, and in the axial direction of the dual enlarged head piston and into a cross-like form, the piston bore 38 and the cylinder-side parallel track assembling port 52 are provided. The space is provided such that the parallel track 12 can be fixed and the crankshaft can be facilitated to assemble, to rotate and to reciprocate, and under the condition that the crankshaft side translation bearing 29 or the crankshaft side cam 40 is mounted on the crankshaft, the crankshaft is inserted and fixed therein. Accordingly, since, when the piston stroke approaches a piston diameter, the parallel track 12 and the crankshaft are protruded to the cylinder side, whereby the parallel track assembling port 52 is extended in the axial direction and in the direction of the periphery by the required amounts. Moreover, the crankshaft is pivoted outside the cylinder by the bearing unit 47 rotatably freely respectively. With reference to Fig.13, the embodiment of the energy conservation cycle engines of various type is described. This embodiment is adapted to the very-small-scale or the small-scale engine. Since the combustion chamber is small, the chamber tends to be cooled, whereby this embodiment is not adapted to the water-injection. In this embodiment, the turbo charger 37 is used in order to respond to such combustion. By the exhaust gas energy from the main combustion chamber with the expanded diameter 24, the turbo charger 37 is driven. First, the air A sucked and compressed by the turbo charger 37 is supplied to the main combustion chamber with the expanded diameter 24, and is, at completion of the compression stroke, supplied from the main combustion chamber with the expanded diameter 24 to the main combustion chamber with the reduced diameter 25. Since a large amount of air is compressed to be supplied into the main combustion condition, even in the very-small-scale or the small-scale engine, the output can be increased. With reference to Fig.14, another embodiment of the energy conservation cycle engines of various type is described. This embodiment is adapted to the small-scale or a middle-scale engine. In the small-scale or the middle-scale engine, although using the adiabatic combustion chamber, the water-injection becomes possible, a second embodiment is most adapted. Soon after combustion, when the water heated in the exhaust section as required is supplied to the combustion chamber, the combustion causing neither NOx nor the uncombusted portion can be realized. By the exhaust gas energy from the main combustion chamber with the expanded diameter 24, the turbo charger 37 is driven. At this time, when the combustion gas is expanded up to atmospheric pressure, the water vapor contained in the combustion gas is expanded, whereby the driving force of the turbo charger 37 is increased. This water vapor was expanded by vaporization latent heat of 540 calorie up to 1700 times. The air sucked and compressed more than usual by the turbo charger 37 is supplied to the main combustion chamber with the expanded diameter 24, and is, at completion of the compression process, supplied from the main combustion chamber with the expanded diameter 24 to the main combustion chamber with the reduced diameter 25. Since the turbo charger 37 is driven by water vapor, the output can be increased. With reference to Fig.15, still another embodiment of the energy conservation cycle engines of various type is described. This embodiment is adapted to the small-scale or a middle-scale engine. In the case of the large combustion chamber, the adiabatic combustion chamber is facilitated to constitute. Moreover, since in the adiabatic combustion chamber exceeding a certain volume, the combustion temperature exceeds 3500 °C, so that the combustion pressure also is increased, by water injecting NOx can be eliminate completely. Soon after combustion, when the water heated by an exhaust-section heat exchanger means 18 and a reduced diameter section heat exchanger means 19 is supplied to the combustion chamber as required, the combustion causing neither NOx nor the uncombusted portion can be realized. By the exhaust gas energy from the main combustion chamber with the expanded diameter 24, the turbo charger 37 is driven. At this time, when the combustion gas is expanded up to atmospheric pressure, the water vapor contained in the combustion gas is expanded, whereby the driving force of the turbo charger 37 is increased. This water vapor was expanded by vaporization latent heat of 540 calorie up to 1700 times. The air sucked and compressed more than usual by the turbo charger 37 is supplied to the main combustion chamber with the expanded diameter 24 and is, at completion of the compression stroke, supplied from the main combustion chamber with the expanded diameter 24 to the main combustion chamber with the reduced diameter 25, Since the turbo charger 37 is driven by water vapor, moreover, the combustion temperature and the combustion pressure also are increased, the output can be increased. With reference to Fig.16, a further embodiment of the energy conservation cycle engines of various type is described. This embodiment is adapted to a large-scale or a very-large-scale engine. In the large-scale or the very-large-scale engine, the adiabatic combustion chamber is essentially required. Since in the large-scale adiabatic combustion chamber exceeding a certain volume, the combustion temperature exceeds 3500 °C so that the combustion pressure also is increased, NOx is increased. Moreover, the combustion time is extended. Therefore, by injecting the water as high temperature as possible in high amounts, the combustion temperature is reduced, thereby NOx being able to be eliminated completely . Soon after combustion, when the water heated by an exhaust-section heat exchanger means 18, a reduced diameter section heat exchanger means 19 and the combustion section heat exchanger means 20 is supplied to the combustion chamber as required, the combustion causing neither NOx nor the uncombusted portion can be realized. By the exhaust gas energy from the combustion chamber, the turbo charger 37 is driven. When the combustion gas is expanded up to atmospheric pressure, the water vapor contained in the combustion gas is expanded, whereby the driving force of the turbo charger 37 is increased. This water vapor was expanded by vaporization latent heat of 540 calorie up to 1700 times. The air sucked and compressed extensively than usual by the turbo charger 37 is supplied to the main combustion chamber with the expanded diameter 24, and is, at completion of the compression stroke, supplied from the main combustion chamber with the expanded diameter 24 to the main combustion chamber with the reduced diameter 25. As described above, for a heat supplying for feeding a hot water or the like, an exhaust heat recovery heat exchanger means is provided separately on the exhaust section, and in the case that the exhaust-section heat exchanger means 18 is provided, the exhaust heat recovery beat exchanger means is preferably provided on the downstream section thereof. Moreover, since for the great improvement of the compression ratio, the shortened stroke engine or a very-shortened stroke engine is preferable, between the downstream section of the turbo charger and the upper flow section of the combustion chamber with the expanded diameter, a mechanical supercharger can be added-in, or the engagement synchronous means 17 can be used both as the mechanical supercharger. In the case of further improving the compression ratio greatly, the energy conservation cycle internal combustion engines type F or type G are used and by addition of the piston supercharger, the compression ratio is improved greatly. Moreover, when improving the compression ratio greatly, the embodiment common to the energy conservation cycle engines type D, type E, type F and type G is realized, the piston stroke is formed into the approximate piston diameter, the parallel track 12 is extended outside the cylinder and the piston length is elongated by the required amounts. INDUSTRIAL APPLICABILITY According to the invention, by providing two combustion chambers using the specifically-shaped piston and cylinder, the thermal energy can be used as rotating energy effectively. Moreover, at least a part of the cup-like recess of the piston is formed into a linear form, and on the cylinder of the piston, an scavenging port and an exhaust port are provided, whereby a scavenging effect can be improved. Furthermore, according to the invention in which, a main combustion chamber with the reduced diameter having a tapered reduced diameter portion which is reduced, for example, up to one fifth in diameter is provided with an one-way air channel, thereby an isolation combustion being realized, there are the large effects as follows : (1) since the combustion during a period of the isolation can be approached to a constant volume combustion up to twenty-five times as compared with the prior art, NOx and an uncombusted portion can be eliminated completely and environmental pollution can be reduced ; (2) a steam and internal combustion coalition engine which water-injection is provided additionally can be realized, whereby NOx and an uncombusted portion can be eliminated completely, moreover, by an increase in speed-type mass energy using water easy to compress and an increase in volume-type speed energy which is expanded by vaporization latent heat of 540 calorie up to 1700 times, NOx can be reduced ; (3) by adding-in a tapered reduced diameter portion, at releasing of the isolation combustion, a combustion-gas jet flow which is high pressure is injected into the cup-like recess effectively and correctly, whereby a rotating force can be increased. Moreover, the combustion is designed to be performed while being churned by a difference in pressure, whereby the uncombusted portion can be eliminated completely ; (4) the influences of a maximum combustion pressure and an abnormal combustion are reduced to one twenty-fifth. The friction loss and vibration are reduced. The equivalent to a minimum bearing load also is reduced to one twenty-fifth as compared with the prior art. Since the maximum bearing load is reduced from a maximum combustion pressure to a maximum compression pressure, by increasing the maximum compression pressure, NOx can be reduced ; (5) since a high pressure combustion chamber becomes the isolation combustion which is reduced up to one fifth in diameter, the high pressure combustion chamber that the main combustion chamber with the reduced diameter is reduced to one fifth in wall thickness and in weight can be realized. The combustion chamber with the expanded diameter becomes the thin-walled combustion chamber which is reduced in pressure and temperature by a large amount, whereby, a specific weight per output can be reduced in weight as compared with the prior art by a large amount; (6) without reference to a kind of fuels, a fuel ignition system, the number of cycles, a scavenging system and a type of the engines, the improvement of a combusting method, the increase in rotating force and the reduction in a specific weight per output can be achieved ; and (7) when by the reciprocating motion of the dual enlarged head piston, the crankshaft is rotated directly to produce rotating power, the component count can be reduced by a large amount to simplify the structure, as well as a compact and lightweight, high-power and low fuel economy system is realized. (8) A shape of a piston is formed into a stepped shape in which from a portion which the diameter is expanded having a cup-like recess, a portion which the diameter is reduced is protruded and a cylinder head is formed into a shape capable of accepting said piston to fit, said shape defining a first combustion chamber and a second combustion chamber, whereby especially, injection of large amounts of water can be performed, so that an abnormal combustion which is most difficult in the case of hydrogen fuel can be eliminated, or even though the abnormal combustion were occurred, the influence can be reduced to nearby one twenty-fifth, whereby especially, in the case that the hydrogen fuel is used, an excellent performance can be expected The energy conservation cycle engine according to the invention as described above, a power transmission device is provided thereon, thereby being able to be used in driving various instruments such as a ship, a vehicle, an electric power generator and an agricultural machinery effectively.

Claims: An energy conservation cycle engine comprising a first piston (22), a first combustion chamber (25) defined by a second piston (23) and a cylinder head, and a second combustion chamber (24) defined by a cup-like recess disposed at the top of the first piston and the cylinder, wherein the second piston protrudes from the recess, the cylinder head is formed to fit the second piston, and the second combustion chamber communicates with the first combustion chamber through a one-way air channel (4) having a check valve (3). An engine according to claim 1, wherein the first piston (22) has cup-like-recesses at both ends, the engine further comprising first combustion chambers (25) defined by second pistons (23) protruding from said recesses, and cylinder heads which conform with the second pistons, and second combustion chambers (24) defined by said recesses and cylinder heads, one-way air channels (4) having check valves (3) communicating with each first and second combustion chamber, and a crankshaft coupled with the centre of the first piston to produce rotating power. An engine according to claim 1 or claim 2, wherein the base of the or each second piston is formed into a tapered-shape, and wherein the associated cylinder head is formed with a complementary tapered lower end. An engine according to any one of claims 1 to 3, wherein the or each second piston (23) has annular projections (6) perpendicular to the axis of that piston. An engine according to any one of claims 1 to 4, wherein the or each second piston (23) has a plurality of grooves (15) extending obliquely to the axis of that piston at the upper portion thereof. An engine according to any one of claims 1 to 5, wherein the gap between the first piston (22) and the cylinder head becomes almost zero at top dead centre. An engine according to any one of claims I to 6, wherein a part of the or each cup-like recess of the first piston (22) consists of a straight line. An engine according to any one of claims 1 to 7, wherein the cylinder is provided with a scavenging port (34) and an exhaust port (33). An engine according to any one of claims 1 to 8, wherein a crankshaft is connected to the first piston (22) to produce rotating power. An engine according to claim 2, or any one of claims 3 to 8, when appendant to claim 2, wherein the second combustion chambers (24) and the first combustion chambers (25) communicate before and after top dead centre through the one-way air channels (4), the engine further comprising a pendulum arm connected to the first piston (22) which rotates the crankshaft to produce rotating power. An engine according to claim 2, or any one of claims 3 to 8 when appendant to claim 2, wherein the second combustion chambers (24) and the first combustion chambers (25) communicate before and after top dead centre through the one-way air channels (4), and a reciprocating motion is converted to rotating power by a crankshaft. An engine according to claim 2, or any one of claims 3 to 8 when appendant to claim 2, wherein the dual enlarged head (first) piston (22) is disposed with its heads at opposite ends thereof, the first combustion chambers (25) and the second combustion chambers (24) communicate before and after top dead centre through the one-way air channels (4), and the engine further comprises a pendulum arm connected with the first piston which rotates the crankshaft to produce rotating power. An engine according to claim 2, or any one of claims 3 to 8 when appendant to claim 2, wherein the dual enlarged head (first) piston (22) is disposed with its heads at opposite ends thereof, each outer end of the piston having a cup-like recess, second pistons (23) protruding from said recesses, and wherein the first combustion chambers (25) and the second combustion chambers (24) communicate before and after top dead centre through the one-way air channels (4), a crankshaft being provided to produce rotating power. An engine according to claims 2, or any one of claims 3 to 8 when appendant to claim 2, wherein the dual enlarged head (first) piston (22) is disposed with its heads at opposite ends thereof, each inner end of the piston having a cup-like recess, the second pistons (23) protruding from said recesses, and wherein first combustion chambers (25) and the second combustion chambers (24) communicate before and after top dead centre, through the one-way air channels (4), a crankshaft being provided to produce rotating power. An engine according to claim 13, wherein supercharging pistons (44) are disposed on the insides of the heads of the dual enlarged head piston (22), and charging valves (45) and feed valves (46) are provided on the piston superchargers. An engine according to claim 14, wherein supercharging pistons (44) are disposed on the outsides of the heads of the dual enlarged head piston (22) and charging valves (45) and feed valves (46) are provided on the piston superchargers. An engine according to claim 2, or any one of claims 3 to 16 when appendant to claim 2, wherein, in order to rotate crankshaft by reciprocating motion of the dual enlarged head piston (22) in a radial direction adjacent to the central position of the inside of the dual enlarged head piston, the piston is provided with oppositely-disposed parallel tracks (12), into which crankshaft-side cams are fitted and pivoted rotatably to the crankshaft so as to be inserted and retained in a manner to reciprocate freely. An engine according to claim 2, or any one of claims 3 to 17 when appendant to claim 2, wherein, in order to rotate the crankshaft by reciprocating motion of the dual enlarged head piston (22) in a radial direction adjacent to the central position of the inside of the dual enlarged head piston, the piston is provided with oppositely-disposed parallel tracks (12), into which cranskshaft side translation bearings (29) are fitted and pivoted rotatably to the crankshaft so as to be inserted and retained in a manner to reciprocate freely. An engine according to claim 2, or any one of claims 3 to 18 when appendant to claim 2, wherein, in order to rotate the crankshaft by reciprocating motion of the dual enlarged head piston (22) in a radial direction adjacent to the central position of the cylinder, cylinder bores (16) and cylinder-side parallel track assembling ports (52) are provided a cross-like form. An engine according to claim 2, or any of claims 3 to 19 when appendant to claim 2, wherein, in order to rotate the crankshaft by reciprocating motion of the dual enlarged head piston (22) in a radial direction adjacent to the central position of the dual enlarged head piston, a piston bore (38) and the piston-side parallel track assembling port (52) are provided in a cross-like form. An engine according to any one of claims 10 to 12, wherein, in order to rotate the crankshaft by reciprocating motion of the dual enlarged head piston in a radial direction adjacent to the central position of the dual enlarged head piston (22), the piston is provided with a parallel track (12) for inserting and retaining a pendulum side cam (39), the upper end of the pendulum arm being supported by a body side cam (13) in a manner to pendulate freely the pendulum arm hanging by the body side by the reciprocating motion of the dual enlarged head piston, the crankshaft side cam (40) being pivoted in the pendulum side parallel track (48) of the pendulum arm for reciprocal motion, and the crankshaft being rotatably born by the crankshaft side cam so as to freely rotate to produce rotating power. An engine according to any one of claims 10 to 12, wherein, in order to rotate the crankshaft by reciprocating motion of the dual enlarged head piston (22) in the radial direction adjacent to the central position of the dual enlarged head piston, the piston is provided with a parallel track (12) for inserting and retaining a pendulum side translation bearing (53), the pendulum arm hanging by the body side cam (13) to pendulate by the reciprocating motion of the dual enlarged head piston, a crankshaft side translation bearing (29) being pivoted in the pendulum side parallel track (48) of the pendulum arm for reciprocal motion, and the crankshaft being pivoted by the crankshaft side translation bearing (29) so as to freely rotate to produce rotating power. An engine according to any one of claims 9 to 14, wherein, in order to rotate the crankshaft, the number of cylinders including second combustion chambers is increased in increments of two cylinders (such as two cylinders, four cylinders and six cylinders), whereby the multiplication in the number of cylinders can be realised unlimitedly. An engine according to claim 11 or claim 12, wherein, in order to rotate the respective crankshaft, the number of cylinders including second combustion chambers is increased in increments of four cylinders (such as four cylinders, eight cylinders and twelve cylinders), whereby the multiplication in the number of cylinders can be realised unlimitedly. An engine according to any one of claims 11 to 14, wherein an engagement synchronous means (17) for synchronising opposite reciprocating motions of the dual enlarged head pistons (22) provided on the respective crankshafts to synchronise the opposite reciprocating motions of the dual enlarged head pistons. An engine according to any one of claims 12 to 14, wherein the engagement synchronous means (17) for synchronising the opposite reciprocating motions of the dual enlarged head pistons (22) is used as a mechanical supercharger. An engine according to claim 2, or any one of claims 3 to 26 when appendant to claim 2, wherein a vicinity of each first combustion chamber (25) is provided as a heat resistant, corrosion resistant and heat insulating structure by a heat-resisting and corrosion-resistant material (21) and a heat insulating material (41); and, on the heat resisting and corrosion resisting materials (21), the appropriate number of inclined air passages (14) of the one-way air channel (4) are provided. An engine according to any one of claims 1 to 27, further comprising a fuel injection device (5) for injecting fuel to the or each first combustion chamber (25), and the injected fuel forms turbulence with the air flowing in through the inclined air passage (14). An engine according to any one of claims 1 to 28, wherein the or each second piston (23) and the required recess (1) are provided as a heat resistant, corrosion resistant and heat insulation structure by heat resisting and corrosion resisting materials (21) and heat insulating materials (41). An engine according to any one of claims 1 to 29, wherein, by providing the one-way air channel on the or each first combustion chamber (25) having a tapered reduced diameter portion, the isolation combustion in said first combustion chamber is released at the optimal timing, thereby greatly reducing the vibration and the maximum bearing load, the high pressure combustion chamber is defined into a small diameter, whereby a reduction in the wall thickness and in weight is realised, as well as reducing the weight of the or each second combustion chamber (24) thereby realising a thin-walled combustion chamber low in pressure and low in temperature. An engine according to any one of claims 1 to 30, further comprising a water injection means (42) on the isolation combustion in the or each first combustion chamber (25); in an exhaust-section heat exchanger means (18) for pre-heating the water, a reduced diameter section heat exchanger means (19), and a combustion section heat exchanger means (20).

Inventors: TANIGAWA HIROYASU, TANIGAWA KAZUNAGA, TANIGAWA, HIROYASU, TANIGAWA, KAZUNAGA
Applicants: TANIGAWA HIROYASU, TANIGAWA KAZUNAGA, TANIGAWA, HIROYASU, TANIGAWA, KAZUNAGA
Application year: 1997
Main classification: F02B19
IPC codes: F02B23, F02B19, F02B3