JP2001355401A - Spherical rotary piston engine - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide an internal combustion piston engine of high piston speed and high output, applying a spherical body as a basic structure. SOLUTION: A rotary piston 30 and a swash plate 40 are connected in the shape of a hinge in a housing 10 and mounted on two planes intersecting at the center of sphere O of a spherical inner wall 11. Then a rotary main spindle 20 inserted into the rotary piston 30 to be pivoted like a pin joint, is fitted and inserted into a main bearing 13 mounted on a wall of the housing 10, and a ring 43 of the swash plate 40 is rotatably fitted to an orbital clearance 12 around a center of the housing 10 inner wall while applying a straight line intersecting with an axial straight line of the rotary main spindle 20 with an angle θ at the center of sphere O as a formed axis. Whereby the rotary piston 30 revolving on the center of sphere O between the swash plate 40 and the axis of the rotary main spindle 20 is paired with the swash plate to be cooperated and rotated. A wall of the housing 10 faced to an operating chamber Fu has an intake hole In, an exhaust hole Ex, valves for opening and closing these holes, and an igniter Ig.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a lightweight, compact, high-speed, high-rotation equal-power, high-output rotary piston engine that solves a reciprocating mass inertia caused by reciprocation of a piston in an internal combustion piston engine.

[0002]

2. Description of the Related Art At present, two-stroke cycle or four-stroke cycle motors are various general-purpose engines including a spark ignition engine of a reciprocating cutting piston engine (hereinafter referred to as a reciprocating piston engine) and a diesel engine for injecting fuel into compressed air. Exists as Although it is very small, 50 to 10
As a small gasoline automobile engine of about 0 ps, combining the envelope of a two-section epitrochoid curve and its inner envelope 4
There is a Wankel institution in the process cycle.

A reciprocating piston engine generally includes a cylinder (cylinder block, liner, cylinder head,
Main components such as crankcases), pistons, connecting rods (connecting rods), crankshafts, flywheels (flywheels), and fuel system devices such as carburetors, suction and exhaust, cooling devices, ignition devices, starting devices, etc. And the four-stroke cycle engine is provided with a valve and its valve gear. The diesel engine has a fuel supply device such as a fuel injection pump or a fuel injection valve instead of a carburetor or an ignition device.

In these components, a piston of an inner cylinder corresponding to a pressure-receiving piece is fitted with a cylinder as an outer cylinder. The piston has a sealing function with a cylinder wall surface, adjustment of a lubricating oil film, heat radiation of the piston, and the like. A piston ring, or piston ring, is mounted to serve the function of receiving the expansion pressure associated with the combustion of the medium in the cylinder and converting the thermal energy into reciprocating motion as linear motion of mechanical energy. Next, the reciprocating motion is transmitted to the connecting rod that makes an arc-like movement via the piston pin, and the large end of the connecting rod is connected to the crankpin, and the crankshaft converts the linear reciprocating motion of the piston into a circular motion. Is what you do. Also, there is a multi-cylinder engine having a plurality of cylinders from the viewpoint of increasing the engine output, reducing vibration, and reducing torque fluctuation.

[0005] The Wankel engine has an arc-shaped contour formed of an internal envelope of a two-section epitrochoid in a cylindrical rotor housing having a two-section epitrochoid inner peripheral surface corresponding to a cylinder block of a reciprocating piston engine. A triangular rotor having three sides of a plane has a rotor bearing formed in a circular hole penetrating a central portion of the triangular shape, and a trochoid phase gear of an internal gear mounted in the circular hole. Is provided. Further, a rod-shaped sealing element attached to each apex of the triangular rotor comes into contact with the inner peripheral surface of the rotor housing, and the inner peripheral surface, the arcuate contour surface of the rotor, and the wall surface of the side housing covering both sides make the three-sided seal element three-dimensional. Form a working chamber.

The two nodes of the epitrochoid whose working chamber volume is minimum correspond to the piston top dead center of the reciprocating piston engine, one of which is in charge of the combustion chamber.
The combustion gas pressure of the combustion chamber that generates the torque acts on the eccentric shaft of the eccentric shaft inserted into the rotor bearing while being applied to the arcuate contour surface of the rotor, as a cutting line direction of the rotation trajectory and the bearing load of the eccentric shaft. In addition, with the fixed external gear mounted on the side housing that meshes with the trochoid phase gear of the rotor, the rotor always performs a planetary motion that revolves and revolves along the epitrochoid curve of the rotor housing with the rotation of the rotor. The rotor rotates in the same direction with a rotation ratio of 1 and the eccentric shaft as the engine shaft with a rotation ratio of 3.

[0007]

2. Description of the Related Art The reciprocating piston engine of the prior art described above has the following problems, or the following limitations in engine performance which must be pointed out as problems associated with higher performance of the engine. . That is, in general, the engine performance is the power (PS) and the fuel consumption rate (g / PS · h). However, the high-performance internal combustion piston engine required at present has a high output, and It must be economical, have low emissions, be harmless, be lightweight and compact, and be quiet.However, under the conditions of high performance, the performance of engines is often incompatible with each other, For example, power and fuel consumption performance, power and quietness (vibration and noise), power and exhaust gas purification, and high power can lead to an increase in engine size, weight, and an increase in the capacity of auxiliary equipment.

[0008] Factors for improving the output of an engine include a stroke volume (l), an average effective pressure (kg / cm ² ), and an engine speed (rpm).
The prime mover having the smallest volume weight per unit output is a gasoline engine, which requires a large specific power of PS / l. However, the increase in output due to the large displacement that increases the stroke volume is not suitable in modern times, and the specific output does not always increase, so it cannot be said that the performance is high. Inevitably, the average effective pressure must be increased, the engine speed must be increased, or both.

[0009] The high rotation increases the amount of work per unit time to achieve high output, but the rotation speed is limited by the piston speed. That is, the shorter the stroke, the higher the rotation can be obtained, but the higher the rotation, the higher the friction loss, that is, the friction loss, increases in a quadratic curve. As a result, the net horsepower reaches a maximum value at a certain rotation speed. The average effective pressure is the average value of the pressure in the cylinder that greatly changes during one cycle, and is proportional to the intake efficiency of the intake air weight. From the above, the output is proportional to the rotation speed and the suction efficiency, but as the rotation speed increases, the suction air flow resistance increases and the suction efficiency decreases.

The working angles of the intake and exhaust greatly overlap due to the inertia of the air flow. Backflow, intake and exhaust interference occur, and the amount of intake air decreases to lower the torque. Conversely, when the suction efficiency is increased in the low rotation range, the suction efficiency in the high rotation range decreases. In addition, the single suction operation takes only a short time of one hundred vehicles, the residual gas in the combustion chamber, the back pressure of various accessories, etc. It is not possible to inhale just enough air or air-fuel mixture. Accordingly, obtaining a high output is nothing less than increasing the intake air weight, that is, improving the suction efficiency.

While improving the volumetric efficiency of the intake air is a means of increasing the average effective pressure, the average effective pressure is also greatly affected by the thermal efficiency. Thermal efficiency increases with compression ratio, and the rate of increase in thermal efficiency increases gradually, but increasing the effective heat increases net pressure and improves fuel economy. After all, a high compression ratio engine has high performance, but on the other hand, in a gasoline engine, high temperature and high pressure due to high compression facilitate occurrence of abnormal combustion. Specifically, knocking, a type of spontaneous ignition, causes the durability of each engine bearing to deteriorate due to the impact of forced vibration, and the high-temperature heat that must be converted to effective power due to intense pressure vibration of the combustion gas is generated. A large amount of heat is transferred to the combustion chamber, which heats the engine and causes fatal damage such as melting of pistons and valves, thermal deformation of cylinders, deterioration of lubricating oil, seizure of pistons and cylinders due to breakage of oil film, etc. .

Further, combustion products at high temperatures undergo an endothermic reaction, and thermal dissociation proceeds as the temperature rises, and the generation of harmful combustion gases such as nitrogen oxides increases. In other words, knocking measures such as a spherical combustion chamber in a gasoline engine, a central arrangement of a spark plug, and an enhancement of swirl and squish flow increase harmful nitrogen oxides (NOx). Increases thermal efficiency but will be limited by knocking. In addition, among the calories of the amount of fuel calories burned in the cylinder, the net thermal efficiency of gasoline engines that can be effectively used as net output is only about 30% (35% for diesel engines), If a high thermal efficiency level is required for high output, even at high compression, the engine will inevitably overheat, improving the performance and size of the cooling system, strengthening the rigidity and strength specific gravity of each part, and taking measures against oil temperature rise. It is necessary, and in that sense, it does not meet the requirements of high performance.

The malfunction of the reciprocating piston engine results from the linear reciprocation of the piston in the cylinder. That is, if the moving part is an axisymmetric rotating body, the centrifugal force acting as an inertial resistance for performing a constant-velocity circular motion balances with the centripetal force, so that no vibration occurs in the engine. However, the reciprocating acceleration motion of the piston that is periodically repeated impairs the balance that should eliminate the effects of the inertial force of the reciprocating mass and the inertial couple, causing engine vibration. In particular, a high-speed engine cannot be put to practical use without means for engine balance, and a single-cylinder engine cannot completely cancel the inertial force even by the balance weight.

The primary and secondary inertia forces and inertia couple balance from a six-cylinder engine having six cranks on a crankshaft. In a four-cycle in-line four-cylinder engine, two reciprocating masses are symmetrically shifted. The primary inertial forces cancel each other out by turning them on, but secondary inertial forces are generated, so if a secondary inertial force balancing device is installed there, the weight increase, high production cost, and complexity are correspondingly increased. I can't deny that. Or,
It is necessary to use a multi-cylinder engine in order to reduce the output increase and the torque fluctuation, and the multi-cylinder engine inevitably increases the volume of the entire engine such as weight and dimensions.

In the case of a long rotating shaft such as a six or eight-cylinder in-line engine, if the regular rotating force applied to one rotation of the shaft is synchronized with the natural vibration of the rotating shaft itself, severe natural vibration that causes shaft destruction will occur. In order to prevent the occurrence of vibrations, a steady rest (damper) of the shaft is required, and each piston is connected to the rotating shaft via a piston pin, a connecting rod, and a crank, so that the number of the same parts is increased. In addition, the intake and exhaust valves are limited at the top of the cylindrical cylinder to limit the intake air weight, and individual parts are used to improve the intake and exhaust efficiency and reduce the inertial mass of the valve train. In any case, there is a disadvantage to the disassembly and assembly workability.

Alternatively, in a reciprocating piston engine, the static pressure is converted into a rotational force with respect to the dynamic pressure of a gas turbine, which is the same internal combustion engine. A large amount of nitrogen oxide (NOx), which is a gas, is generated. In addition, the piston speed of the reciprocating piston engine can be increased as the stroke length of the oversquare of the stroke / inner diameter ratio becomes smaller. In addition, the vibration and noise due to the increase in the inertial mass of the reciprocating motion described above increase, and similarly, the valve device also generates abnormal vibration as the engine speed increases, thereby preventing the engine from rotating at a high speed. Deviation reduces intake and exhaust efficiency, makes it easier for the valve and piston to interfere with each other, and eventually causes the valve and piston to collide and destroy the engine itself, narrowing the practical rotation range of the average piston speed. I have.

Summarizing the above, a disadvantage of a reciprocating piston engine is that its operation is unavoidable due to the inertial mass of the reciprocating parts such as pistons, connecting rods, valves and the like. In other words, high rotation for high output is prevented, the operating rotation range is narrow, engine vibration and noise are large, the structure is complicated, and the engine volume is large. Another problem is that a large amount of nitrogen oxide (NOx), which is difficult to purify, is generated.

Next, the drawbacks of the Wankel engine are as follows: the suction and combustion parts are not the same, and the working chamber consisting of the housing and the rotor is formed of a flat or flat plate. The combustion chamber wall is not cooled by the intake fresh air, the temperature difference between the intake side and the combustion side of the engine is large, and the apex seal at the apex of the rotor cannot follow the bimetallic thermally deformed wall surface. Further, since the working chamber has a rectangular cross section, it is impossible to maintain perfect airtightness due to a change in the cross-sectional area, and there is a remarkable leakage loss and a remarkable frictional wear due to the inability to form an oil film by oil film lubrication.

Naturally, these indicate an increase or deterioration of the consumption rate of fuel or lubricating oil in combination with the problem in principle.
Forcible emission of unburned gas due to incomplete combustion, blow-through, dilution gas, poor flame propagation, etc., raises the harmful CO and oxidants, the HC value which is the cause of so-called photochemical smog, to an extremely high level. In addition, parts and mechanisms lack simplicity, are difficult to understand, require less manufacturing errors and high assembly accuracy, are expensive and have poor durability, have poor airtightness, and have poor combustion chamber shapes. not compatible.

[0020]

SUMMARY OF THE INVENTION Accordingly, the present invention has been made in view of the aforementioned limitations and problems of the conventional internal combustion piston engine,
In addition to meeting the indispensable conditions of internal combustion engine such as output, fuel consumption, exhaust gas, quietness, durability, weight size, production cost, etc., it eliminates the reciprocation of the piston, that is, the pressure receiving piece, and Is to provide a novel internal combustion piston engine having a completely different basic structure and having various performances superior to conventional engines.

[0021]

SUMMARY OF THE INVENTION The present invention has the characteristic of a basic structure that is formed on a geometrical figure in a geometrical configuration of interrelated points, lines, and surfaces.

[0022]

According to one aspect of the present invention, there is provided a housing 10 formed on an inner wall surface having a radius r from a spherical center O and forming a spherical surface G and having an angle θ. Two fixed axis straight lines intersecting at the center O are defined as an X axis and a Y axis, a point at which the X axis intersects the spherical surface G is defined as P, and a point at which the Y axis intersects the spherical surface G is defined as Q. Let U be the conical trajectory having the spherical center O as the vertex with the bottom of the space between Q as Q, the axial line perpendicular to the X axis at the spherical center O as the M axis, and forming a horizontal plane on the X axis and its diameter line A great circle plane in the spherical surface G having the axis of rotation L as the rotation axis is an R circular surface, and a great circle plane formed through the spherical center O in the spherical surface G with the Y axis as a vertical axis is an S circular surface. , The intersecting line where the R and S circles intersect at the spherical center O is defined as the axis K, To both ends of the dividing line K points Ka, the point Kb.

As described above, in the housing 10 in which the relations of points, lines and surfaces are set, the inner wall of the housing 10 on the extended plane of the S-circle is cut into the raceway groove 12 of the orbital groove, and the X-axis passes through it. Main bearings 13 and 13 are provided on a wall facing the housing 10. The main bearings 13 are provided with a rotating main shaft 2 having a straight shaft shape.
0, which is located at the ball center O of the rotating main shaft 20 and which is a pin post of a pin joint joint 55 having an M axis as a connection axis or a pin receiving hole. To have.

On the R-circular surface, a housing 1 forming a spherical surface G
0, a spherical arc surface 32 of the opposing outer peripheral surface rotatably contacting the inner wall surface,
32 and the front and back arcuate surfaces 31, 31, 31, 3 which form an arcuate contour plane of the spherical arc surfaces 32, 32 and have the K-axis side as a chord.
1 and a substantially circular plate-shaped rotating piston 30 having a columnar piston intermediate shaft 33 interposed and combined on its chord side. The rotary piston 30 is provided with a piston through hole 34 for allowing the rotary main shaft 20 to be loosely inserted into both spherical arc surfaces 32, 32.
In addition, the center of the shaft 25
Is provided so as to pivotably pivot within a range of ± θ with respect to the rotary main shaft 20 on the X-axis, and the point K at both ends of the piston intermediate shaft 33 is provided.
a, Hinge pins 51 and 5 of a hinge joint 50 element on the point Kb side.
1, or hinge pin receivers 52, 52 are provided.

Also, on the S-circle surface, an arcuate surface 4 on both sides.
The two arcuate plates formed from the first, the first, the 41 and the 41 and the chord side surfaces 42 and 42 facing each other in sliding contact with the column surface of the piston intermediate shaft 33 so as to be rotatable in the raceway 12. A circular plate-shaped swash plate 40 having an outer peripheral surface formed by combining the fitted annular swash plate rings 43 is arranged. This swash plate 40
The connecting element corresponding to the hinge joint 50 element is provided on both sides of the swash plate ring 43 located on the side of the point Ka and the point Kb to be fitted, and the hinge joint 50 rotates with the swash plate 40. The piston 30 and the crossing line K are hingedly connected to each other so that the piston 30 can slide in the ± θ angle range.

Then, the inclined plate 40 on the S-circle surface is
The inner wall surface of the housing 10 is closed to form two hemispherical working chambers Ha, Ha composed of hemispherical constant volume spaces. Are formed in four working chambers Fu, Fu, Fu, Fu forming two comb-shaped spaces. Furthermore, a suction hole In and a discharge hole Ex for the working medium facing the half-moon-shaped working chambers Ha, Ha, and a valve device Va for opening and closing the passage of the working medium appropriately are provided. Or a spherical rotary piston engine having a fuel injection valve inserted therein.

[0027]

According to another aspect of the present invention, a spherical center O, a radius r,
Spherical surface G, angle θ, axis X, axis Y, point P, point Q, conical trajectory U, axis M, axis L, R circular surface, S circular surface, intersection dividing line K,
Each relationship between the point Ka, the point Kb, the line, and the surface is set.

The housing 10 in which the relationship between the point, the line and the surface is set is divided into two sides by a parallel plane of the S-circle, and the working chamber portion of the hemispherical space having the inner wall surface of the spherical surface G and the Y-axis A main bearing 13 is provided on the wall of the housing 10 through which the X-axis passes through and formed in the raceway space 12 of the concave space having an inner peripheral surface with an inner diameter longer than the radius r of the concentric circle. The main bearing 13 is made to bear the shaft and neck of the rotating main shaft 20 having a straight shaft shape, and is located at the spherical center O of the rotating main shaft 20 and is a pin post of the pin joint joint 55 having the M axis as a connection axis, or A shaft center 25 formed by one of the pin receiving holes is provided.

On the R circular surface, a spherical arc surface 32 of an outer peripheral surface rotatably contacting the inner wall surface of the housing 10 of the spherical surface G, and an arcuate contour plane of the spherical arc surface 32 are formed, and the K axis side is a chord. A rotating piston 30 of a substantially semi-circular shape, in which front and back arcuate surfaces 31 and 31 and a columnar piston intermediate shaft 33 are combined on the chord side thereof, is arranged. The rotary piston 30 has a piston through hole 34 for allowing the rotary main shaft 20 to be loosely inserted into the arcuate surface 32, and the piston intermediate shaft 3 of the piston through hole 34.
A piston pivot 35 of a connecting element corresponding to the axis central pivot 25 is provided at a central portion in the center 3 so as to swingably pivot within a range of ± θ angle with respect to the rotary main shaft 20 on the X-axis, A hinge joint 5 is provided at the points Ka and Kb on both ends of the shaft 33.
0 element hinge pin 51, 51 or hinge pin receiver 52,
52 are provided.

Further, on the S-circle surface, arcuate surfaces 41, 41 are provided on both sides of the piston intermediate shaft 33 on the K axis, and a sliding contact between the arcuate surfaces 41, 41 and the column surface of the piston intermediate shaft 33 is provided. A circular plate formed by a chordal side surface 42 formed of a groove-shaped concave surface to be engaged and an outer sliding contact surface 45 in which the back surfaces of both arcuate surfaces 41 and 41 are formed on the same rotation surface, is rotated by the raceway gap 12. A circular swash plate 40 having an outer peripheral surface formed by combining annular skewing plate rings 43 that fit together is disposed. The skew plate 40 has a skew plate ring 4 located on the side of the points Ka and Kb.
A connecting element corresponding to the hinge joint 50 element is provided and fitted on both sides opposite to each other, and the hinge joint 50 intersects the swash plate 40 and the rotating piston 30 with the dividing line K as a hinge axis ±± θ.
It is connected to the angle range so that it can move freely.

Then, the skew plate 40 on the S-circle surface is
The inner wall surface of the housing 10 is closed to form a semilunar working chamber Ha composed of a hemispherical constant volume space, and the rotating piston 30 on the R-circle forms a comb-shaped space. It is formed in two working chambers Fu, Fu. Furthermore, the suction hole In and the discharge hole E of the working medium face the half-moon working chamber Ha.
x and a valve device V for opening and closing the passage of the working medium as appropriate
a, and a spherical rotary piston engine characterized by inserting an igniter Ig or a fuel injection valve into the combustion chamber.

[0032]

Another solution is that a spherical center O, a radius r, a spherical surface G,
Angle θ, axis X, axis Y, point P, point Q, conical locus U, axis M, axis L, R circular surface, S circular surface, cross secant K, point Ka,
The relation between the point Kb, the line, and the surface is set.

The housing 10 on which the relations of the points, lines, and planes are set as described above is provided on the housing 1 on the S-circular extension plane.
The main bearings 13 and 13 are provided on the opposing wall of the housing 10 through which the X-axis penetrates by forming a raceway gap 12 of the circumferential groove on the inner wall surface circumference. A rotary spindle 2 having a straight shaft shape on the main bearings 13, 13.
0, which is located at the spherical center O of the rotating main shaft 20 and which is either a pin post of a pin joint joint 55 having an M axis as a connecting axis or a pin receiving hole. To have.

On the R-circular surface, a spherical arc surface 32 of a rotating outer peripheral surface larger than a hemispheric surface straddling the S-circle surface in a rotatable manner on the inner wall surface of the housing 10 of the spherical surface G, and an arcuate contour of the spherical arc surface 32 Bow-shaped surfaces 3 on both sides where the chord sides sandwich the K axis line in a plane
The rotating piston 30, which is a hemispherical circular plate, in which a cylindrical piston intermediate shaft 33 is half-embedded and united between the arcuate surfaces 31, 31 on both sides thereof, is arranged. The rotary piston 30 has the rotary spindle 2
A piston shaft hole 34 for allowing the zero to be inserted is opened, and a piston shaft 35 of a connection element corresponding to the shaft center shaft 25 is provided at the center of the piston shaft hole 34 so that the rotation main shaft 20 on the X axis is formed. A range of ± θ angle is pivotably connected to the piston intermediate shaft 33, and the points Ka and K at both ends of the piston intermediate shaft 33.
Hinge pins 51, 51 or hinge pin receivers 52, 52 of the hinge joint 50 element are provided on the b side.

On the S-circle surface, the front and back arcuate surfaces 41,
The raceway gap 12 is formed in an arc-shaped plate formed by a piston intermediate shaft 41 and a chord side surface 42 in sliding contact with the column surface of the piston intermediate shaft 33.
A circular plate-shaped swash plate 40 having an outer peripheral surface formed by combining an annular swash plate ring 43 rotatably fitted with the swash plate is disposed. The swash plate 40 is provided with connecting elements corresponding to the hinge joint 50 elements on opposite sides of the swash plate ring 43 located on the side of the points Ka and Kb, and fitted together. The swash plate 40 and the rotating piston 30 are slidably connected to each other in a ± θ angle range using a crossing line K as a hinge axis.

Then, the skew plate 40 on the S-circle surface is
, Two hemispherical working chambers Ha, Ha composed of hemispherical spaces are formed on both sides of the inner wall surface of the housing 10, and each of the half-moon working chambers Ha, Ha Are formed in the working chambers Fu, Fu forming a comb-shaped space. Furthermore, a suction hole In and a discharge hole Ex for the working medium facing the half-moon-shaped working chambers Ha, Ha, and a valve device Va for opening and closing the passage of the working medium appropriately are provided. Or a spherical rotary piston engine having a fuel injection valve inserted therein.

[0037]

Another solution is that a spherical center O, a radius r, a spherical surface G,
Angle θ, axis X, axis Y, point P, point Q, conical locus U, axis M, axis L, R circular surface, S circular surface, cross secant K, point Ka,
The relation between the point Kb, the line, and the surface is set.

The housing 10 in which the relations of the points, lines and surfaces are set is divided into two sides by a parallel plane of an S-circle, and the working chamber portion of a hemispherical space having an inner wall surface of a spherical surface G and a Y-axis line A main bearing 13 is provided on the wall of the housing 10 through which the X-axis passes through and formed in the raceway space 12 of the concave space having an inner peripheral surface with an inner diameter longer than the radius r of the concentric circle. The main bearing 13 is made to bear the shaft and neck of the rotating main shaft 20 having a straight shaft shape, and is located at the spherical center O of the rotating main shaft 20 and is a pin post of the pin joint joint 55 having the M axis as a connection axis, or A shaft center 25 formed by one of the pin receiving holes is provided.

On the R circular surface, a spherical arc surface 32 of an outer peripheral surface rotatably in contact with the inner wall surface of the housing 10 of the spherical surface G, and an arcuate contour plane of the spherical arc surface 32 are formed, and the K axis side is a chord. A rotating piston 30 of a substantially semi-circular shape, in which front and back arcuate surfaces 31 and 31 and a columnar piston intermediate shaft 33 are combined on the chord side thereof, is arranged. The rotary piston 30 has a piston through hole 34 for allowing the rotary main shaft 20 to be loosely inserted into the arcuate surface 32, and the piston intermediate shaft 3 of the piston through hole 34.
A piston pivot 35 of a connecting element corresponding to the axis central pivot 25 is provided at a central portion in the center 3 so as to swingably pivot within a range of ± θ angle with respect to the rotary main shaft 20 on the X-axis, A hinge joint 5 is provided at the points Ka and Kb on both ends of the shaft 33.
0 element hinge pins 51, 51 or hinge pin receivers 52, 5
2 is provided.

Further, on the S-circle surface, arcuate surfaces 41, 41 are provided on both sides of the piston intermediate shaft 33 on the K axis, and a sliding contact relationship between the arcuate surfaces 41, 41 and the columnar surface of the piston intermediate shaft 33 is provided. A circular plate formed by a chordal side surface 42 formed of a groove-shaped concave surface and a contour sliding contact surface 45 having the back surfaces of the two arcuate surfaces 41 and 41 formed on the same rotation surface is rotated by the raceway gap 12. A circular swash plate 40 having an outer peripheral surface formed by combining annular skewing plate rings 43 that fit together is disposed. The skew plate 40 has a skew plate ring 4 located on the side of the points Ka and Kb.
A connecting element corresponding to the hinge joint 50 element is provided and fitted on both sides opposite to each other, and the hinge joint 50 intersects the swash plate 40 and the rotating piston 30 with the dividing line K as a hinge axis ±± θ.
It is connected to the angle range so that it can move freely.

The element composition including the rotating piston 30, the swash plate 40, and the rotating main shaft 20 in the housing 10 configured as described above is set to one set, and another set similar to the components is formed. The two sets of compositions are connected in parallel or in series that can be linked.

Then, the skew plate 4 on both S, S circular surfaces
0, 40 are the housings 10 of the spherical surfaces G, G provided by each other.
Are closed to form hemispherical working chambers Ha, Ha each consisting of a hemispherical constant volume space. The working chambers 30 and 30 form two working chambers Fu, Fu, Fu, and Fu each forming a comb-shaped space. Furthermore, a suction hole In and a discharge hole Ex for the working medium facing the half-moon-shaped working chambers Ha, Ha, and a valve device Va for opening and closing the passage of the working medium appropriately are provided. Or a spherical rotary piston engine having a fuel injection valve inserted therein.

[0043]

DETAILED DESCRIPTION OF THE INVENTION The present invention has the characteristic of a basic structure that is based on geometrical figures in the geometric arrangement of points, lines, and surfaces that are interrelated in principle. Hereinafter, embodiments of the present invention will be described with reference to the drawings.

First, FIG. 1 shows an interrelation pattern defining the present invention. In a housing 10 formed on an inner wall surface which forms a spherical surface G with a radius r from a spherical center O, an angle .theta. Two fixed axis straight lines intersecting at O are defined as an X axis and a Y axis, a point at which the X axis intersects the spherical surface G is defined as P, and a point at which the Y axis intersects the spherical surface G is defined as Q. Let U be the conical trajectory whose conical generatrix circumscribes the side circumference of the cone having the spherical center O as the apex with the diameter of the base as the diameter of the bottom, and further define the axial straight line orthogonal to the X axis at the spherical center O as the M axis, and A large circular plane in a spherical surface G having a horizontal plane with the X axis as the axis of rotation of the diameter line of the diameter L is defined as an R circular surface, and a spherical center O is defined in the spherical surface G with the Y axis as a vertical axis.
Is defined as an S-circle, and an intersection line where the R-circle and the S-circle intersect at the spherical center O is defined as an axis K.
Then, both ends of the intersecting line K are referred to as a point Ka and a point Kb, and the respective relationships between the point, the line, and the surface are set as described above.

When the X axis and the Y axis are regarded as the fixed position localization axes and the X and Y axes are simultaneously rotated, the Y axis is obtained.
The S-circle, which is a vertical plane of the axis, rotates while maintaining the phase, and the R-circle, which has the axis L as the rotation axis, has the base O between the points P and Q on the X and Y axes, and the spherical center O has a conical shape. 1 to 2 and 3 on a conical trajectory U which is a vertex while rotating in the order shown in FIGS. 1 and 2, and at 90 degrees of the rotation, the rotation axis L of the R-circular surface is on the X-axis as shown in FIGS. The semicircle revolves and moves on the Y-axis, and in the rotation of 90 degrees, the remaining semicircle locus is drawn from the Y-axis via FIG. 4 and returns to the X-axis in FIG. In other words, if the rotation axis L of the R-circle revolves (revolves) around the circumference of the conical trajectory U, the R-circle rotates by 180 degrees, which is a half rotation, to change the front and back.

At this time, the rotation axis L of the R surface and the intersection line K are always orthogonal to each other at the spherical center O, and the gap formed between the intersecting R and S surfaces is R. When the rotation axis L of the circular surface is on the X-axis, the vertical angle on the obtuse angle side becomes 90 + θ and becomes maximum (the spaces B and D in FIG. 1 and the spaces A and A in FIG. 5).
C), and the apex angle on the acute angle side becomes 90-θ, which is the minimum (spaces A and C in FIG. 1 and spaces B and D in FIG. 5). In other words, the R-circle surface and the S-circle surface approach each other at a half turn, separate at the next half turn, and approach or separate at each turn as a hinge axis and a fulcrum of the intersection line K as a hinge. Repeat the separation.

Referring to the closed spaces A, B, C, and D surrounded by the spherical surface G, the R circular surface, and the S circular surface, the rotation axis L in FIG. In FIG. 5 which makes a half turn, the space A expands and the space B contracts, the space C expands and the space D contracts. Further, the space A contracts and the space B expands, the space C contracts and the space D expands in the half rotation of the original FIG. 1 through FIGS. 5 to 6, 7 and 8. That is,
When the space A expands, the space B contracts and when the space C expands, the space D contracts. The space D contracts when the space A expands, and the space C expands when the space B contracts. Therefore, the spaces A and B form a pair by changing the increase / decrease of the volume of each other inversely proportionally, and the spaces C and D also pair by changing the volume of each other inversely proportionally, and the spaces A and C and the spaces B and D There is an opposing relationship opposite to the order in which the volume changes are directly proportional.

The points, lines, surfaces, and spaces A, B, C, D (comb-shaped operation chambers Fu, Fu, Fu, F
Various embodiments of the present invention will be described below with reference to the drawings based on the relationships u). 9 to 18, which illustrate the various embodiments, the suction port In and the discharge port Ex for allowing the working medium to flow in and out, the valve device Va, the ignition device (or fuel injection valve) Ig, and the like are shown. In all the drawings for explaining the invention, a sealing device such as a gas seal and an oil seal (a piston ring in a reciprocating piston engine), a cooling device,
The illustration of the lubrication device and the like is omitted.

[0049]

[Embodiment 1] As shown in FIGS. 9 and 10, one of the embodiments is an embodiment based on the structure of the above-mentioned solving means 1. FIG. That is, in the same manner as in the above-described solution 1, in the above-described relationship in which the point, the line, and the surface are set, the housing 10 in which the relationship of the point, the line, and the surface is set is, for example, aa, aa shown in FIG. BB is divided into a central part and parts on both sides thereof by two parallel cut planes sandwiching the S-plane of bb,
The central portion thereof is formed in an annular swash plate housing 10b having an inner wall concentric with an S-circle surface larger than the spherical surface G, and both side portions face each other with concave inner walls 11, 11 each formed of a symmetrical spherical surface G. The half-moon-shaped rotating piston housings 10a, 10a are formed. Then, the rotating piston housings 10a, 10a on both sides thereof and the oblique plate housing 10b at the center are formed into a unitary spherical structure.

Then, the two rotating piston housings 10a, 10a having the inner surface of the oblique plate housing 10b as the groove bottom.
A space between the circumferential edges of the concave inner walls 11, 11 is formed as a raceway gap 12 in a groove-shaped gap corresponding to a circumference along an extension plane of the S-shaped surface. In addition, the main bearings 13 formed of circular holes are formed in opposing walls of the rotary piston housings 10a, 10a through which the X axis passes.
13 are provided. The main bearings 13, 13 are formed with journals having both shaft necks of a rotary main shaft 20 having a straight axis with the X axis as a rotation axis, and the journal portions are fitted and rotatably supported. The rotary spindle 20 has a connecting element (in FIGS. 9 and 10) formed of either a pin post or a pin receiving hole of the pin joint joint 55 which is located at the spherical center O and uses the M axis as a connecting axis. (Which is a pin receiving hole).

That is, if a hollow sphere having an inner surface formed by a spherical surface is cut by two parallel cut planes sandwiching the great circle plane of the sphere, a half-moon-shaped volume in which a cylindrical central portion and a bowl shape face each other is obtained. It is divided into three parts on both sides of the container. The spherical shell before the cutting is the whole of the housing 10, and the both sides of the spherical concave inner walls 11, 11 facing each other are the rotating piston 3.
Rotating piston housing 10 containing semicircles of 0 each
If the central portion has a larger inner diameter than the inner diameter of the spherical inner surface of the concave inner walls 11, 11 of the rotary piston housings 10a, 10a, the central portion will be described below if it is hollowed out and formed in a concentric circle. The skew plate housing 10b stores the skew plate ring 43 of the skew plate 40 to be formed.

Therefore, if the three parts are combined to form an overall shape, the inside of the swash plate housing 10b is formed as a raceway space 12 in which the groove-shaped recessed portion orbits the center of the housing 10. , And main bearings 1 on opposite sides
Nos. 3 and 13 pass through the spherical center O of the hollow sphere described above, open an arbitrary inclination angle θ other than the horizontal zero degree and the right angle with respect to the axis (Y axis) of the two cut planes, and intersect at the spherical center O. Piston housing 10 on a straight line (X axis)
a, 10a.

Then, on the R-circle surface, the biconcave inner walls 11, 1 forming the spherical surface G of the rotary piston housings 10a, 10a.
Spherical arc surfaces 32, 32 of the opposing outer peripheral surface rotatably contacting 1
And the front and back arcuate surfaces 31, 31, 31, 31 forming the arcuate contour plane of the spherical arc surfaces 32, 32, and the front and back arcuate surfaces 3
Two meniscal plates formed from the chordal sides held by the bowed strings 1, 31, 31, 31 are symmetrically arranged with their chordal sides facing each other with the K axis line interposed therebetween, and the chords of each other are arranged. Cylindrical piston intermediate shaft 3 with K axis attached to the side
The rotating piston 30 of a substantially circular plate with the 3 interposed and united is arranged.

The rotating piston 30 penetrates through the center of the piston intermediate shaft 33 from the two arcuate surfaces 32, 32 on the X-axis along the R-circle included in the rotating piston 30 to allow the rotating main shaft 20 to play. The through hole 34 is opened. In the center of the piston intermediate shaft 33, a piston pivot 35 (see FIGS.
In this case, a pin column is provided. The piston pivot 35 is pivotally connected to the rotary main shaft 20 on the X-axis as a base line so as to swing within a range of ± θ in correspondence with the central shaft 25 of the rotary main shaft 20. . Further, the piston intermediate shaft 33 on the side of the points Ka and Kb
At both ends, one of the hinge pins 51, 51 of the hinge joint 50 or the hinge pin receivers 52, 52 (in FIGS. 9 and 10, the hinge pin receivers 52, 52 each having a circular hole formed in the center of both bottom surfaces). Is provided).

That is, the rotating piston 30 is formed such that a spherical body rotatably fitted into the above-described housing 10 having a spherical hollow inside has a center plane defined by a plane passing through the spherical center of the spherical body.
If the both sides are symmetrically cut out and formed in a plate shape, and a cylindrical body is formed in the diameter part of the center plane to be the piston intermediate shaft 33, the comb shape is symmetrical on both sides with the piston intermediate shaft 33 as the symmetric axis. The entire shape of a substantially circular plate having a meniscus shape is formed. That is, each of the meniscuses is formed in the shape of a piston wing, and the rotating and centrifugal sides of the two piston wings are the spherical arc surfaces 32, 32, which are spherical surfaces remaining without being cut off,
The two spherical arc surfaces 32, 32 are brought into sliding contact with the concave inner walls 11, 11 of the rotary piston housings 10a, 10a provided by them, respectively, in a non-immediate manner.

Accordingly, if the rotary piston 30 is formed into the shape as described above by cutting out the upper and lower parts of a sphere serving as a base body of the rotary piston 30, the plane shape is circular, and the center line of the great circle plane included in the circle is included. Is the axis of the piston intermediate shaft 33, the two wings of the piston blade are symmetrically formed on both sides of the piston intermediate shaft 33 with the piston intermediate shaft 33 as a symmetric axis as described above. The rotary piston 30 is provided with a hole that penetrates the inside of the above-described great circle plane. The through hole is formed on the edge of the great circle plane that the rotation piston 30 includes, with the inside center of the piston intermediate shaft 33 as a fulcrum. A fixed portion of the circumference of the part is defined as the point of action of the movable end, and is a piston through hole 34 which is elongated in the direction of the great circle and presents a flat space. Each of the 32 has an oval opening.

The rotating spindle 20 which enters through the piston blade window and penetrates the piston passage hole 34 is formed by a circular center 2 which is a circular body attached to the center of the rotating spindle 20.
5 is a shaft center pivot 25 with the center in the piston intermediate shaft 33 as a fulcrum.
And a pivot surface of a rotating piston 30 formed on a rotating surface of a shape that completely agrees with the geometric conditions, and the M axis is connected to the joint base shaft 25 and the piston shaft 35 by the two pieces of the shaft central shaft 25 and the piston shaft 35 which are fitted to each other. A connecting portion of the pin joint joint 55 as a line is formed. In addition, the rotating main shaft 20 has a round bar having a diameter slightly smaller than the short diameter of the piston through-hole 34 in order to loosely insert the piston through-hole 34, and is vertically connected to both opposing sides of the shaft center pivot 25 to form a straight shaft. In addition, both shaft necks are formed in a journal for fitting the main bearings 13 and 13 of the walls of the rotating piston housings 10a and 10a, and are rotatably supported by bearings.

On the other hand, on the S-circle surface, the same arcuate surfaces 41, 4 corresponding to the both-side arcuate surfaces 31, 31, respectively, of the rotary piston 30 are provided on both sides opposite to each other with the piston intermediate shaft 33 on the K axis line interposed therebetween.
1 is arranged symmetrically on the front and back sides and has a chord side surface 42 whose geometrical condition is slidably engaged with the axial column surface of the piston intermediate shaft 33, and the raceway gap is formed on the arcuate contour surface of both the arcuate plates. A skewing plate 40 formed into a circular plate by combining an annular swash plate ring 43 that is fitted to the slidable member 12 and is rotatably slidable is disposed.
In other words, the skew plate 40 is composed of two half-moon plates, each having a smaller arc-shaped semicircle with arcuate arcs facing each other with their respective arcuate contours facing outward and the chordal sides 42, 42 facing each other, and both of them. Since the circular plate is formed on the same plane with a cylindrical sloping plate ring 43 formed on the inner peripheral surface which is in contact with the two arcuate contour surfaces and arranged outside the two meniscus plates, the K axis line A window-like gap penetrating in a rectangular shape on the K-axis line by four sides facing the chordal sides 42, 42 facing each other with the interposition therebetween and the inside both sides of the oblique plate ring 43 facing the points Ka, Kb. With parts.

Further, the hinge pins 51, 5 of the pin pillars are provided with the cross secant line K as an axis of attachment at the points Ka, Kb of the window-shaped gap.
1 is protruded and fixed inward, and then the piston intermediate shaft 33 of the rotary piston 30 is fitted into the window-like space along the axial column direction. The column surface of the intermediate shaft 33 is sealed in a sliding contact relationship, the both bottom surfaces of the piston intermediate shaft 33 and both opposing surfaces of the oblique plate ring 43 remaining as a window frame are also sealed in a sliding contact relationship, and the piston intermediate shaft 33 is closed.
Hinge pins 51, 51 are attached to the hinge pin receivers 52, 52 at both ends.
Are fitted together to form the hinge joint 50, and the rotating piston 30 and the swash plate 40 are slidably connected in the ± θ angle range with the cross secant line K as the hinge axis.

The rotating piston 30 thus assembled
Rotating piston housing 1 which is given to each other by half circles
0a, 10a, and the swash plate ring 43 of the skewing plate 40 is incorporated into the raceway 12 of the skewing plate housing 10b in a freely rotatable fitting state. But,
Bi-concave inner wall 1 of rotating piston housings 10a, 10a
1 and 11 are closed to form hemispherical semi-circular working chambers Ha, Ha on both sides thereof, and each of the two semi-lunar working chambers Ha, Ha is connected to a rotating piston 30 on an R-shaped surface. But,
Four working chambers Fu, Fu, Fu, Fu (two air chambers A, B,
C, D). Further, the two half-moon working chambers Ha,
A suction hole In and a discharge hole Ex for allowing the working medium to flow in and out facing Ha and a valve device Va for opening and closing the passage of the working medium as appropriate are provided.
g, or insert a fuel injection valve.

Then, the working medium is sucked and compressed in the process of increasing the volume of each comb-shaped working chamber Fu (air chambers A, B, C, D) shown in FIGS. When the working medium is ignited and burned near the top dead center, the space between the rotating piston 30 and the two arcuate surfaces 31 and 41 of the swash plate 40 is expanded by the expansion pressure, and the rotating piston 3
Numeral 0 moves in the direction of the force while being constrained from the plane of rotation of the swash plate 40 under the pressure of the expanding combustion gas, and pivots while rotating in the range of an angle (θ × 2) about the M axis. The rotating spindle 20 is rotated.

[0062]

Second Embodiment Four comb-shaped working chambers Fu, Fu, Fu, and F in the housing 10 according to the first embodiment.
u is a single-comb working chamber to a three-comb working chamber Fu,
Although it is possible to operate in place of Fu, Fu or Fu, Fu, Fu, the second embodiment is different from the circular plate rotating piston 30 in the first embodiment in FIGS. As shown in FIG. 12, a semi-circular rotating piston 3 is provided in one semi-lunar working chamber Ha in one spherical housing 10.
0 based on the configuration of the solution means 2 configured to operate in the air chambers A, B or the air chambers C, D of the two comb-shaped operating chambers Fu, Fu arranged in a direction perpendicular to the rotation axis. It is a form of.

That is, similar to the solution 2,
For each set relationship of lines and faces,
When the housing 10 in which the relationship between the line and the surface is set is divided into two by a cut plane parallel to the S-circle a-a shown in FIG. A row-plate housing 10b and a half-moon-shaped rotary piston housing 10a in which a concave inner wall 11 made of a spherical surface G faces the inner wall surface of the concave space, and the rotary piston housing 10a and the skew-plate housing 10b When they are combined into an integral structure, a concave gap of the swash plate housing 10b is formed as an orbital gap 12 on the inner peripheral surface of a circle concentric with the Y axis, but in this embodiment also, a rotary piston through which the X axis passes. A main bearing 13 extends through the wall of the housing 10a at a point P, and the main bearing 13 is located at the spherical center O and is connected to a connecting element of the pin joint joint 55 (in FIGS. A is) rotate thereby freely fitted inserted the bearing neck journal of the rotary shaft 20 which has a JikuHisashikururu 25 forms a straight shaft-like receiving hole.

A substantially semi-circular rotary piston 30 having a column of a piston intermediate shaft 33 integrated on the chordal surface of the semi-circular plate is disposed on the R circular surface. Also, a piston through-hole 34 for penetrating the rotary main shaft 20 from the spherical arc surface 32 through the inside of the piston intermediate shaft 33 is opened, and the pin joint joint is formed at the center of the piston through-hole 34 in the piston intermediate shaft 33. A piston pivot 35 composed of 55 pin-like elements is provided to be pivotally connected to the central axis 25 of the rotary main shaft 20, and a coupling element of a hinge joint 50 is provided at both ends of the piston intermediate shaft 33 (in FIGS. The hinge pin receivers 52, 52 are provided.

Further, the swash plate 40 disposed on the S-circle surface
Is a piston intermediate shaft between two arcuate surfaces 41, 41 on the same plate surface corresponding to the front and back arcuate surfaces 31, 31 of the semicircular rotary piston 30, and the arcuate chord side of the arcuate surfaces 41, 41 sandwiching the K axis. A chordal side surface 42 of a semi-cylindrical concave surface formed in a groove-like concave portion which is slidably engaged with the axial column surface of the shaft 33, and a chordal side surface 4 thereof.
A circular plate having an outer sliding contact surface 45 in which the back surfaces of both arcuate surfaces 41, 41 including the two are formed on the same rotation surface, is fitted to the outer peripheral surface of the circular plate so as to be rotatable and slidable in the raceway 12. Is a circular plate united with the swash plate ring 43 of FIG. In addition, the skew plate ring 4 located on the side of the points Ka and Kb is also provided on the skew plate 40.
3 are provided with hinge pins 51, 51 of connecting elements to be applied to the hinge joints 50 at both ends of the piston intermediate shaft 33, and the chordal side surface 42 formed of a groove-shaped concave surface of the inclined plate 40 is provided.
When the piston intermediate shaft 33 is inserted along the direction of the shaft column, the swash plate 40 and the rotating piston 30 form and connect a hinge joint 50 on the K axis.

As a result, the second embodiment is different from the housing 10
Into one half, and one of them is formed on the inner wall surface 11 of the concave spherical surface to form a rotary piston housing 10a that encloses the spherical arc surface 32 of the rotary piston 30 having a substantially semi-circular shape, and the other half has a half-moon-shaped operation. It is configured as a swash plate housing 10b that holds a circular swash plate 40, which is a surface on which the chamber Ha is formed, and two comb-shaped operation chambers A and B or C and D are formed. However, as shown in FIGS. 11 and 12, the main bearings 13 and 13 provided on the X-axis of the wall of the rotating piston housing 10a and the wall of the skew plate housing 10b are fitted with both shaft necks of the rotating main shaft 20. The two main shafts of the rotary main shaft 20 are inserted into a main bearing 13 provided through the wall of the rotary piston housing 10a on the X-axis, with only one of the two columns being inserted,
The swash plate 40 is provided with a pattern-shaped swash plate shaft 46 at the center of the outer sliding contact surface 45 and is fitted into the skewing plate bearing 14 penetrating the wall of the skewing plate housing 10b on the Y axis. There is.

[0067]

[Embodiment 3] Another embodiment is based on the structure of the above-mentioned solving means 3, and is shown in FIGS.
As shown in FIG. 5, this embodiment is different from the first embodiment in that the four comb-shaped working chambers Fu, Fu, Fu, Fu (air chambers A, B, C, D) are replaced with axial horizontal shafts inside the spherical housing 10. Operating chambers Fu, Fu (air chambers A, D)
Or, it is constructed and operated in the air chambers B and C). Therefore, only the shapes of the rotating piston 30 and the swash plate 40 are different in the configuration, and
The formation of the inside and the outside, the connection between the rotary main shaft 20 and the rotary piston 30, the connection between the rotary piston 30 and the swash plate 40, and other configurations and operations are completely the same as those in the first embodiment.

In other words, the rotary piston 30 arranged on the R-circular surface in the housing 10 has the two-sided surfaces each having the arcuate surfaces 31, 31, 31, 31 on both sides in the first embodiment.
In this embodiment, the arcuate surface 32 of the rotation outer peripheral surface larger than the hemispherical surface in contact with the spherical surface G, and the arcuate shapes on both sides on the same plate surface that forms the arcuate contour plane of the arcuate surface 32 in this embodiment. It is a substantially circular plate formed into a hemispherical body from the surfaces 31, 31 and a cylindrical piston intermediate shaft 33 that is merged in a semi-embedded manner on the K axis between the arcuate surfaces 31, 31 on both sides thereof. In this hemispherical rotary piston 30 as well, a piston through hole 34 through which the rotary main shaft 20 is loosely inserted is opened along the R-circular surface, and the rotary main shaft 20
The pivot joint 25 is pivotally connected to form a pin joint joint 55, and a connecting element of a hinge joint 50 is provided at both ends of the piston intermediate shaft 33 (in FIG. 14, hinge pin receivers 52, 52 having the centers of both bottom surfaces pierced). Is). The hemispherical rotary piston 30 has a double arcuate surface 3 within the hemisphere.
The shape of the back surface side of 1, 31 is not limited to a hemispherical surface, and is free.

The swash plate 40 placed on the S-plane is
In contrast to the above-described first embodiment of the circular plate in which two bow-shaped plates are integrated with the skew plate ring 43, in this embodiment, the skew plate ring 4
3 is a circular plate having a window-shaped gap that is larger than a semicircle with the chord side surface 42 as a side and has a chord side 42 as a side on the K axis, and a rotating piston 30 is provided in the window. Of the piston intermediate shaft 33 having hinge pins 51, 51 on opposed inner side surfaces of the swash plate ring 43 which are located on the points Ka, Kb side, respectively. The hinge pin receivers 52 are connected and fitted. As a result, the air chambers A and D or the air chambers B and C are formed on both sides of the swash plate 40 in the housing 10.

[0070]

Fourth Embodiment The two working chambers Fu and Fu (the air chambers A and B or the air chambers C and D) in the second embodiment are combined into four housings in one housing 10. Room F
u, Fu, Fu, and Fu (air chambers A, B, C, and D) can be configured and operated. In other words, this embodiment shown in FIGS. 15 and 16 has a housing 10 in which the points, lines, and surfaces are set in the same manner as the construction of the solution 2, and a semicircular plate rotating piston incorporated in the housing 10. 30
The element composition of the second embodiment of the skew plate 40 and the rotary spindle 20 is defined as one set, and another set that is completely the same as the components is formed into two sets, and the two sets are combined. Are connected and operated at the center in the housing 10 where both are united.

That is, the skew plates 40, 40 on the S, S circle surface
Each provide a rotating piston housing 10
a, the semi-lunar working chambers Ha, Ha of constant volume, all of which form a hemisphere by closing the concave inner walls 11, 11;
Each of the semi-lunar working chambers Ha, Ha has two comb-shaped air chambers A, B forming a comb-shaped space whose volume changes in inverse proportion by the semicircular rotating pistons 30, 30 on the R, R circular surfaces. C and D are formed. Then, the suction hole In and the discharge hole E through which the working medium flows in and out of each half-moon shaped working chamber Ha.
x and a valve device V for opening and closing the passage of the working medium as appropriate
a, and an ignition device Ig or a fuel injection valve is inserted while looking into each combustion chamber. In this embodiment, two sets of element compositions in the second embodiment are connected and interlocked. The operation of each set is the same as that of the second embodiment.

The composition of the two sets in the fourth embodiment may be, for example, as shown in FIGS. 61 to 63, whether the two sets are connected by a single rotating spindle 20 formed in a straight axis. Alternatively, as shown in FIG. 57, the two sets are connected by the rotating spindle 20 shared in the center of the housing 10 as shown in FIG.
Alternatively, as shown in FIG. 52 and FIG. 56 or FIG. 53, the skew plates 40 are combined by two sets, or are connected by a skew plate connecting shaft 47 that passes the skew plates 40 and 40 coaxially. Or
As shown in FIG. 65, the gears are connected via a transmission mechanism such as by meshing gears attached to each of the shaft necks. In the connection of the two sets of compositions, the mounting positions of the main bearings 13, 13 in the modes in FIGS. 52 and 56 in which the skew plate 40 is coaxial and the modes in FIGS. Changes in
The rotation phase of the rotating spindles 20, 20 is changed, and the rotating pistons connected to the rotating spindles 20, 20 and the swash plate 30,
The assembling phases of two sets 40, 30, and 40 are relatively changed.

That is, both rotating spindles 20 and 20 in the fourth embodiment have (1) rotating axes parallel to each other on the same plane as shown in FIGS. 53 and 56 (a). (2) As shown in FIG. 56 (c), the tilt angles θ, θ with the skew plates 40, 40 given to each other are the same, or the tilt angles θ with the skew plates 40, 40 given to each other. , Θ are different from each other, and all of them have extension axes intersecting each other on the same plane. (3) As shown in FIG. 56 (a) again after the changes (b) and (c) in FIG. 56 (a), the skewing plate housings 10b, 10b are set with the spheres O, O given by each as the center of rotation. The Y axis of the axis is the axis of rotation, and the axis has axes on two planes that intersect at an arbitrary rotation angle within a range in which each of them makes a half turn in the opposite direction while maintaining the tilt angles θ and θ.

On the other hand, the two sets of compositions are skewed between the modes in FIGS. 57 and 61 to 63 in which the rotating spindle 20 is connected and the modes in FIGS. A change in the axis Y, Y position of either the two axes formed on the inner surfaces of the plate housings 10b, 10b or the two axes of the bearings of the skewed plate shafts 46, 46 changes the rotation piston housing 10a,
Since the centers and directions of the inner walls 11, 11 of the biconcave surfaces 10a are also relatively changed, the two of the inclined plate 40 and the rotating piston 30
The mounting phase of the set is also changed. That is, the fourth embodiment
Are inclined at angles θ, θ.
While the center of rotation is the center of rotation O, O of the concave inner walls 11, 11, which are given to each other, and the axis X of the rotary main shaft 20 is the axis of rotation. The skew plate housings 10b, 10b are assembled in the skew plate housings 10b, 10b having the axis fixed at an arbitrary rotation angle as the axis of formation of the inner surface. There are the following three types of rotation axes 40, 40.

(1) As shown in FIG. 61 (a), they have rotation axes parallel to each other on the same plane (FIGS. 57, 62, 6).
3 and FIG. 65 (c) are similarly illustrated for convenience). (2) As shown in FIG. 61 (c) and FIG. 65 (d), they have rotation axes intersecting each other on the same plane (FIG. 61).
In (a), the skew plates 40, 40 tilt angles θ, θ of each other
May be different). (3) Rotation axes fixed to each other on two planes that intersect at an arbitrary rotation angle (rotate the mounting axis of one of the skewing plates 40 between FIGS. 61A to 61C). This is a case where it is fixed at an arbitrary rotation angle position).

[0076]

[Common mode of each embodiment (θ angle and pin joint joint)]
In any of the above embodiments, the angle θ created when the X axis and the Y axis intersect on the spherical center O is 10 ° <θ.
<60 ° is a practical range, and the optimal angle is 25 ° to 35 °
It is. Further, in any of the above embodiments, the rotating main shaft 20 and the rotating piston 30 are connected via an articulated portion, but the pin joint composed of the shaft center pivot 25 and the piston pivot 35 provided to each other. The embodiment of the joint 55
The configuration in which the rotating spindle 20 has a double-necked neck will be described below.

First, a pin joint joint 55 shown in FIG. 17 is configured such that a center axis 25 of a rotary main shaft 20 formed of a circular body has two shaft columns formed of a round bar fixed to its opposing outer peripheral surface, and a circular hole is formed at the center. The piston pivot 35 of the rotary piston 30 having a pin receiving hole has an internal space formed by an internal surface that meets the geometrical condition with the axial center 25, and a pin post is attached to the center of the internal space. Is formed in the inner space.
5, the pin post of the piston pivot 35 is fitted into the pin receiving hole of the shaft center pivot 25 in a pivotal relationship. Alternatively, although not shown, if the relationship between the piston pivot 35 of the pin post and the shaft center pivot 25 of the pin receiving hole is reversed, pin receiving circular holes are formed on both upper and lower circular faces facing the piston pivot 35. A pin post is formed to project from each of the two circular surfaces of the shaft center pivot 25, and the pin post of the shaft center pivot 25 is fitted into a pin receiving hole of the piston pivot 35. Or, as shown in FIG. 18, the central shaft 25 is formed as a double-sided round pillar,
The piston pivot 35 of the rotary piston 30 is also formed as an inner hollow recess which engages with the round pillar of the shaft center pivot 25 to pivotally connect each other.

Alternatively, as shown in FIG. 19, the rotating spindle 20
A central pivot 25 of a circular plate having the same width or less as to the rotating piston 30 is formed by fixing a round rod of an axial column to each of both opposing side surfaces of the central pivot 25, Numeral 30 denotes two horizontal circular plates which are separated from each other in the horizontal direction and have a gap corresponding to the plate thickness of the shaft center 25 on a horizontal plane passing on the axis of the piston intermediate shaft 33, and are connected to the center of the gap. It is formed with a round pillar piston pivot 35 serving as an axis, and a rotary spindle 20
Of the circular plate shaft center 25 so as to be rotatable, and the shaft center shaft 25
The piston rod 35 of a circular column is fitted in a bearing circular hole that is bored through the center portion of the piston. At this time, the piston intermediate shaft 33 has an axial length exceeding the width of the rotating piston 30, and both ends thereof are hinged pins 5 of the hinge joint 50.
Projection is formed as a shaft and neck of the piston intermediate shaft 33 replacing the shafts 1 and 51, and both shaft and neck are connected to opposite sides of the swash plate ring 43 on the points Ka and Kb side in a shaft support relationship.

[0079]

[Principle of operation] The above-described pin joint joint 55 and hinge joint 50
When the rotating spindle 20 is rotated when the rotating spindle 20, the rotating piston 30, and the swash plate 40 are engaged with each other, the rotating piston 30 moves to the rotating plane of the swash plate 40. Housing 1 which is the common center of the three while being restrained
The conical movement along the conical trajectory U is performed with the spherical center O of the concave inner walls 11 and 11 as the center of rotation. The intermediate shaft 33 slides around as a hinged shaft, and the increase or decrease of the volume generated in each air chamber Fu in the housing 10 as the rotary piston 30 slides is operated as each stroke in the internal combustion piston engine. Next, the operation principle of the spherical rotary piston engine of the present invention will be described.

In the present invention configured as described above, when the swash plate 40 and the rotary spindle 20 rotate on the fixed axis while maintaining the fixed angle θ, the opening of the held θ angle is reduced to the bottom. The rotating piston 30 revolves around the conical trajectory U on the conical peripheral surface on the side. That is, when rotation is given to the rotating spindle 20 into which the main bearing 13 on the X axis is inserted, the rotating piston 30 which is placed on the rotating spindle 20 and has the piston pivot 35 pivotally attached to the central axis 25 of the rotating spindle 20.
Rotates in the same direction together with the rotary main shaft 20 while swinging about the center axis 25 of the movable end.

That is, the rotating piston 30 and the swash plate 40 placed on two planes in the housing 10 that intersect at an angle θ with the sphere O intervene with the intersection line K as the hinge axis. Only the hinge piston 50 is connected with the two pieces of the hinged element 50 so that only the hinge-shaped movement is possible, and when the plates face each other and rotate cooperatively, only the rotating piston 30 is used as the plate surface of the swash plate 40 as the sliding opposing surface. Swings, and only the rotating piston 30 swings with the rotation. When the rotating piston 30 and the rotating main shaft 20 mounted on the same plane are connected by the pin joint joint 55 on the spherical center O, the rotating piston 30
Is limited to only the horizontal direction of the R-plane which is the mounting plane.

From the above, the rotary spindle 20 and the swash plate 40
The rotating piston 30 interposed therebetween has a connecting axis of the pin joint joint 55 connected to the rotating main shaft 20 and a connecting axis of the hinge joint 50 connected to the swash plate 40 orthogonal to each other on the same plane.
It has the same relationship as the cross piece of the universal joint of the prior art in the middle of the shaft, with the spherical center O as the center of rotation, the center line between the rotation axes of the rotary spindle 20 and the swash plate 40 as the rotation axis, A precession axis having the diameter of the turning circumference is provided between the rotation main shaft 20 and the rotation axis of the swash plate 40, and the turning circumference revolves while rotating, and the rotation of the rotation is half a revolution for each revolution. do. As a result, the rotating piston 30 sets the maximum range of the amplitude swing to twice the intersection angle θ between the X and Y axes (θ × 2), and revolves 1 on the X axis of the base shaft, that is, θ angles per half rotation of the rotation ( θ × 1).

The rotation of the rotary piston 30 is shown in FIGS. 20 and 21 using the first embodiment as an example.
Reference numeral 21 denotes a rotating spindle 2 which is interlocked with a pin joint joint 55 interposed therebetween.
0 indicates an operation for half a rotation (180 degrees) of the rotating piston 30, and the rotating directions of the rotating main shaft 20 and the rotating piston 30 are counterclockwise. Now, the rotating piston 30 in FIG. 20 (a) is in a symmetric horizontal equilibrium state on the rotating main shaft 20, and the rotating main shaft 20 is orthogonal to the piston intermediate shaft 33 and overlaps with the center line of the piston passage hole 34. In this state, when the rotating piston 30 is rotated together with the rotating main shaft 20 to advance in the direction from FIG. 20 (i) to (b), the rotating piston 30 rotates on a horizontal equilibrium axis passing through the center of the piston passage hole 34. The axis L gradually comes off from the rotary spindle 20,
Further, through (H) and (N), as shown in FIG. 21 (H), the maximum of the amplitude range is operated to change the phase to the vertical position.

After all, FIG. 20 (i) to FIG. 21 (ho)
Is equivalent to the movement of the tilt angle θ created between the axes of the rotating main shaft 20 and the swash plate 40, and corresponds to the length of the crank arm of the reciprocating piston engine. And the rotation angle of the rotating spindle 20 corresponds to 90 degrees, so a multiple of the angle θ corresponds to the stroke length, and the stroke length swings on the rotating spindle 20 with the pin post of the piston pivot 35 on the M axis as a fulcrum. This is the amplitude range of the moving rotating piston 30, and is the horizontal opening major axis in the space inside the hole of the piston through-hole 34 that spreads in a butterfly shape on the R-circular surface.

Further, the rotary spindle 20 shown in FIG.
And rotate the rotary piston 30 by 90 degrees (F)
After the steps (a) and (c), the rotary spindle 20 and the rotary piston 30 make a half turn (180 degrees) from FIG. The operation equivalent to the stroke was performed,
This corresponds to the amount of movement between the top dead center and the bottom dead center of the piston in the reciprocating piston engine.
Since the rotating pistons 30 in (c) are in the same position and in the same phase, the rotating piston 30 in the spherical rotating piston engine of the present invention has a feature that it has a top dead center and a bottom dead center overlapping the same point.

On the other hand, the arcuate surfaces 31, 41 of the rotary piston 30 and the swash plate 40, which are the surfaces on which the comb-shaped working chamber Fu is formed,
The approach and separation are alternately repeated with the cooperative rotation of the rotary piston 30 and the swash plate 40, and the space volume of the working chamber Fu decreases in the approach and the space volume of the working chamber Fu increases in the separation. The rotation of the rotating piston 30 for half a rotation shifts the working chamber Fu volume from the minimum to the maximum,
In the rotation of the next half rotation, the maximum volume is shifted to the original minimum volume, and the volume of the working chamber Fu repeatedly increases and decreases every half rotation of the rotation. The volume of the working chamber Fu is increased or decreased between two revolutions of the rotating piston 30.
The two revolutions correspond to one rotation.

With respect to the change in the volume of the working chamber Fu, the first and second embodiments and the fourth embodiment described above have two comb-shaped working chambers A and B formed by dividing the same half-moon shaped working chamber Ha into two. Or C and D increase / decrease the volume of each other in inverse proportion, and also in the third embodiment, two comb-shaped working chambers A and D in the same spherical surface G or B and C increase / decrease the volume of each other inversely. In either case, when one of the two comb-shaped working chambers Fu, Fu increases with the rotation of the rotary piston 30, the other decreases, and the decreasing side turns to increase. For example, there is a relationship between the double-ended cylinder and the piston, the increasing side of which decreases.

Further, four strokes of one cycle performed by each working chamber Fu correspond to two rotations of the rotating piston 30, the swash plate 40, and the rotating main shaft 20 which are coaxially connected. The operation is completed after four revolutions of the rotary piston 30. At that time, the air of the working medium is sent to the working chamber Fu, and the supply of heat is given by burning the fuel, and the four strokes of intake, compression, expansion, and exhaust are repeated. Perform the basic cycle of the air cycle. For this purpose, the valve device V mounted on the intake and exhaust holes In and Ex at an appropriate time during one cycle.
a to control the inflow and outflow of the working medium, and synchronize the ignition device Ig or the fuel injection valve (nozzle) appropriately mounted facing the combustion chamber with the optimum rotation angle of the compression stroke. Is burned, the rotating piston 30 of the pressure receiving piece receives the combustion heat and the expansion pressure, moves in the direction of the force, and converts it into a rotating force to rotate the rotating main shaft 20.

The spherical rotating piston engine of the present invention
In the first, third and fourth embodiments, the two semi-lunar working chambers H
a, Ha, in the first, second, and fourth embodiments, any one of the two air chambers Fu, Fu in the same half-moon working chamber Ha is set as the input pressurization side Pu for pumping the working medium,
The output pressure receiving side P that handles the work of thermal work on the other side
It is possible to configure and operate a two-stroke cycle engine designated as o. That is, for each rotation of the rotary piston 30 and the swash plate 40, two air chambers A and B and two air chambers C and D of each half-moon-shaped working chamber Ha (one air chamber A in the third embodiment). And D, or the air chambers B and C), or each of the air chambers A and B, and C and D in the same half-moon working chamber Ha, for approximately two strokes of intake and compression, expansion and exhaust. And a communication hole for communicating the air chambers of the input pump side Pu and the output power side Po with each other.
A valve Va is provided on the communication hole as needed to open and close appropriately, and the working medium is appropriately moved from the input side Pu to the output side Po. In the embodiment, one of the two half-moon working chambers Ha, Ha is used as the input side Pu and the other is used as the output side Po, and the working medium flows from the input side Pu to the output side Po and is given to each other. Fu-Fu, Fu-Fu are air chambers AC and air chambers BD, or air chambers AD and air chambers B-
C, but the former embodiment of the air chamber combination is a two-stroke cycle engine equivalent to Embodiments 16 to 1.
9 will be described later.

Further, as an operation principle of the present invention, FIG. , 23 will be described as an example of the first embodiment.

The operation of the double-end rotary piston 30 incorporated in the half-moon-shaped working chambers Ha, Ha formed in the double-end by the swash plate 40 is performed in the same half-moon-shaped working chamber Ha.
When the volume of one of the two air chambers A and B or the one of the two air chambers C and D is expanded to increase the volume, the air chamber space on the opposite side contracts to reduce the volume. Further, if the two half-moon-shaped working chambers Ha, Ha are formed in the same volume, and each semicircle of the rotary piston 30 is formed in the same volume, the two air chambers A sandwiching the same arcuate surface 41 of the swash plate 40 can be formed. The spaces D, or B and C, also have equal stroke volumes with equal maximum and equal minimum volumes and operate with inversely proportional volume changes. The two air chambers A opposing each other with the skew plate 40 being obliquely interposed therebetween.
And C or B and D operate in an increasing / decreasing relationship in which the volume of each other is always directly proportional.

After all, the comb-shaped space is a plate surface gap between the rotating piston 30 and the skew plate 40 facing each other. However, the space volume increases and decreases due to the separation of the plate surfaces away from and approaching each other. Rotating piston 30 and swash plate 4
The approach of the plate surface with 0 is the contraction of the gap between the plate surfaces and the reduction of the volume of the air chamber. Correspondingly, on the contrary, the separation of the plate surface between the rotating piston 30 and the swash plate 40 is an expansion of the air chamber gap and an increase in the volume of the air chamber. It corresponds to the process of moving to the point, and the relaxation and contraction of the gap formed between the plate surfaces of the air chambers A, B,
The increase and decrease of the volume in C and D.

Referring to FIG. 22A, the air chamber A has the minimum volume in which the air chamber gap is most contracted, and the air chamber C at the symmetrical position of the air chamber A also has the air chamber gap contracted to the minimum. However, the air chamber B sharing the same half-moon operating chamber Ha as the air chamber A has a maximum volume with the air chamber gap expanded, and shares the other half-moon operating chamber Ha with the air chamber C. Like the air chamber B, the air chamber D has a maximum volume in which the air chamber gap is expanded to the upper limit. Then, when rotation in the direction of the arrow is given, each air chamber A, B, C, D
From (A) to (B), (C), (D), (E),
The air chamber volume is gradually changed in the order of (F), and the air chamber spaces of the air chambers A and C therein are expanded to increase the volume, and conversely, the air chambers B and the air chambers are increased. The air chamber space of D shrinks to reduce the air chamber volume. The operation is shown in FIG.
When the object is rotated by 90 degrees starting from, each volume change becomes medium and each volume becomes equal as shown in FIG. 23 (G).

Further, from FIG. 23 (G) to (H), (I),
When the air chambers A and C are sequentially operated in the directions (J) and (K), the air chamber gaps of the air chambers A and C are further expanded to increase the volume, and conversely, the air chambers B and D are further reduced in volume. When the rotating piston 30 in A) makes a half turn corresponding to 180 degrees,
As shown in FIG. 23 (L), the front and back of the rotary piston 30 are switched, so that the air chamber gap between the air chamber A and the air chamber C is maximized. Is converted to Then, rotation is further performed in the same direction until the air gap between the air chambers A and C in FIG. 23 (L) reaches the minimum volume and the air chamber gap between the air chambers B and D also reaches the maximum volume. ,
In FIG. 22 (A), one rotation of 360 degrees is performed, and each of the air chambers A, B, C, and D changes in volume to complete two strokes.

[0095]

[Progress of the Stroke] The spherical rotary piston engine of the present invention can be constructed and operated as a two-stroke cycle engine as described above. There is no harm in configuring and operating a four-stroke engine having a stroke, a compression stroke, an expansion stroke, and an exhaust stroke. Next, the four-stroke operation of each of the air chambers A, B, C, and D in the spherical rotary piston engine of the present invention as the four-stroke cycle engine will be described based on the above-described operation principle. 1
24 and 25 will be described as an example.

Here, the combustion of the working medium and the intake and discharge of the working medium in the internal combustion piston engine will be described. Since the combustion of the air-fuel mixture in the combustion chamber requires a certain time, constant volume combustion cannot be performed. Ignition is performed well before the top dead center of the piston, but generally, when the ignition is performed so that the maximum pressure is about 12 degrees (crank rotation angle) after the top dead center, the work loss due to this cause is minimized. That is,
Normally, it is ignited at about 30 degrees before top dead center, does not burn immediately, but has a waiting time for ignition and starts burning at about 15 degrees before top dead center, and then the cylinder pressure rises sharply, About 10 degrees after the dead center, the combustion finishes and reaches the maximum pressure. When the ignition advance angle is adjusted so that the center between (A) and (B) when the position is (B) is the top dead center, the maximum output is obtained. Also, it takes a certain amount of time to discharge the combustion gas, and if the exhaust valve is opened after continuing expansion to the bottom dead center, there is no room for the pressure in the cylinder to sufficiently decrease due to exhaust gas ejection, and negative work in the exhaust stroke Will be made. Therefore, it is better to open the exhaust valve long before the bottom dead center, reduce the cylinder pressure to near atmospheric pressure by exhaust gas ejection, and move on to the exhaust stroke.Also, in the intake, consider the inertia of high-speed intake air flow. The closing timing of the intake valve is delayed considerably (several tens of degrees at the crank rotation angle) from the bottom dead center. In other words, at the valve timing of opening and closing the valve, the intake valve opens much before the top dead center and closes much after the bottom dead center. Similarly, the exhaust valve opens just before the bottom dead center and well after the top dead center. Since the valve is closed, the operating angles of the intake and exhaust valves largely overlap at the top dead center.

However, each stroke of one cycle in the spherical rotary piston engine of the present invention is, for convenience, at 180 degrees from the rotation angle of 0 degrees of the rotary main shaft 20 replacing the crankshaft of the reciprocating piston engine and entering the intake operation of the supply air. The intake stroke ends and the compression stroke starts, and the compression stroke ends at a rotation angle of 360 degrees. At that time, the compressed working medium is ignited to start the expansion stroke, and the expansion stroke starts rotating. It is assumed that the exhaust stroke is started at the same time as the rotation angle of 540 degrees of the main shaft 20 and the exhaust stroke is ended at the rotation angle of 720 degrees. Therefore, the volume change from the minimum to the maximum or from the maximum to the minimum of each comb-shaped working chamber Fu in the present invention is performed every 180 degrees as the rotation angle of the rotary spindle 20,
The entire operation of the four strokes from the intake stroke to the exhaust stroke is performed at 720 degrees, that is, during two revolutions of the rotary main shaft 20, as in a four-stroke reciprocating piston engine.

A flow path hole as a passage for the working medium is provided as a hole that penetrates a wall of the housing 10 at an appropriate position corresponding to the suction and exhaust strokes of the air chambers A, B, C, and D. A valve device Va for opening and closing the hole is also provided on the flow passage hole. During the intake stroke, the valve Va of the exhaust hole Ex on the air chamber side is closed and the valve Va of the intake hole In is opened. The valve Va of the hole In is closed and the valve Va of the exhaust hole Ex is closed.
The suction and exhaust holes In and E are opened during both the compression and expansion strokes.
x Both valves Va, Va are closed. Furthermore, each air chamber A,
An ignition device Ig or a fuel injection valve in the case of a diesel engine is inserted into the wall of the housing 10 looking into the working chamber where the volumes of B, C and D are minimized.
In the vicinity where the compression strokes of B, C and D reach the maximum, the igniter I
g, or ignites the air-fuel mixture compressed by the fuel injection valve (hereinafter, the fuel injection valve is included in the ignition device Ig,
Only described) to inject or burn fuel into the compressed air, and establish each process consisting of intake of intake air in the internal combustion piston engine, compression of the intake air, combustion and expansion of the compressed air, and discharge of waste air. It is to let.

In FIGS. 24 and 25, for the sake of convenience, the entry of the valve Va is omitted, and only the opening and closing of the operation of the valve Va is described with the inlet and outlet holes In and Ex as a process from the start to the end of the exhaust stroke. However, the symmetrical two-hole set shown in FIGS. 24 and 25 is the intake hole In, the one hole on the rotating spindle 20 is the exhaust hole Ex, and the inflow and outflow holes In and Ex are indicated by solid lines on the front front side in the figure. The broken line indicates the position on the reverse side of the figure, and the igniter Ig is also illustrated only at the time of ignition performed just before the end of the compression stroke of the working medium.

First, FIG. 24 (A) which is a starting point of each process start
In the air chamber A, the exhaust of the combustion gas has now been completed, the intake hole In (the set of two solid lines on the left side in the figure) has been opened, and the rotary piston 30 is at the air supply start position corresponding to the top dead center. At this time, the air chamber B is at the time of the maximum expansion of the full stroke volume and at the same time as the start of the contraction of the air chamber space, and thus is at the start of the discharge of the combustion gas after the expansion stroke. At this point, the intake port In and the exhaust port Ex communicating with the air chamber C and the air chamber D are both closed, and the air chamber D is at the end of the intake stroke having the maximum volume in which the air chamber space is expanded to the upper limit. The air chamber C is at the upper limit of the compression in which the air chamber space is contracted to near the minimum, and the start of the combustion in which the working medium is ignited and the start of the expansion stroke.

The combustion action in the air chamber C is such that the heat of combustion and the expansion pressure spread the space between the rotating piston 30 and the swash plate 40 forming the air chamber C, and the air that has just completed the expansion stroke immediately before. At the same time as applying a rotational force to the rotary spindle 20 in place of the chamber B, the air chamber space of the air chamber A is expanded by moving FIG. 24A in the order of FIGS. It acts to shrink the air chamber gap with the chamber B. After all, the air chamber C in FIG. 24A is an expansion stroke, the air chamber A is an intake stroke, the air chamber B is an exhaust stroke, and the air chamber D is a compression stroke, each of which is in an initial stage of the stroke, From there, Fig. 24 (a), (c)
After (d), the air chambers A, B, C, and D become 180
Each air chamber A,
B, C, and D are completed for one stroke that does not overlap with each other.

That is, when the air chamber A is rotated by 180 degrees, the air chamber gap is reduced to the minimum in FIG.
As shown in the figure, it is located at a position facing the next compression stroke after the intake stroke is completed by expanding to the maximum, and the position where the air chamber B changes from the maximum volume to the minimum volume and starts the intake stroke at the end of the exhaust stroke. It is in. At this time, the intake port In on the side of the half-moon working chamber Ha shared by the air chambers A and B remains open, but the exhaust port Ex is immediately after being closed. FIG.
As shown in (d), immediately after the exhaust valve Va is opened at the position where the air chamber C enters the next exhaust stroke in which the expansion stroke is completed and the air chamber space is expanded to the full stroke amount (one hole on the right side in the drawing). ), The air chamber D is at the position of the rotation angle at which the air chamber space is most contracted to end the compression stroke, but before the end of the compression work, the expansion medium is ignited by the igniter Ig in the expansion stroke. You are in the early stages of combustion.

The heat and expansion pressure in the air chamber D also expands the air chamber gap of the air chamber D formed by the rotating piston 30 and the plate surface of the swash plate 40, and the air chamber B at the position facing the air chamber D is expanded. Of the air chambers A, C, which are relaxed
, And is converted into the rotational force of the rotary spindle 20 following the previous air chamber C. Therefore, FIG.
In (d), the air chamber A advances the compression stroke, the air chamber B advances the intake stroke, and the air chamber C advances the exhaust stroke, all of which are at the beginning of the stroke. And from FIG. 24 (D) to (E),
25 (g) through (f), the air chambers A, B, and B are rotated by exactly one rotation (180 ° × 2) from FIG. 24 (a).
C and D complete the operation for each two strokes. Fig. 25
In (g), the air chambers A and C have the minimum volume of the combustion chamber, which is the gap volume of each other. In the air chamber A, the compressed air converged at the highest time of the compression stroke. It is at the start of the expansion stroke ignited by the igniter Ig.

The expansion stroke in this air chamber A is
In addition to applying a rotational force to 0, the air chamber C acts to expand the air chamber gap and reduce the air chamber gaps of the air chambers B and D.
In FIG. 25 (g), the intake port In opened to the half-moon working chamber Ha on the air chambers A and B side has already been closed and the exhaust port Ex has also been closed. C,
The exhaust hole Ex opening to the half-moon-shaped working chamber Ha on the D side is opened, and the exhaust gas of the combustion chamber D is continuously discharged to the air chamber C after the exhaust stroke, and the air is simultaneously supplied to the air chamber C. Inlet I
n (a pair of two dotted lines on the right side in the figure) has just been opened.
That is, the air chamber C is located at a position where the intake stroke is started at the same time as the end of the exhaust stroke, and the contents of the air chamber are almost empty. At this time, the air chambers B and D are mutually expanded to the maximum. It has a volume, and the air chamber B is at the start position of the next exhaust stroke in which the intake stroke ends and the compression stroke starts, and the air chamber D finishes the expansion stroke and discharges waste air.

Further, from FIG. 25 (g) to (g),
When the air chambers A and C have the maximum air chamber volume when the air chamber A and the air chamber C have the maximum air chamber volume in the order of (e), the air chamber A has already finished the expansion work and the exhaust holes Ex (the left side in the figure). One hole (dotted line) is opened, and the air chamber C is at the start position of the compression stroke for converging the working medium sucked to the full stroke volume. On the other hand, of the air chambers B and D both of which contract the air chamber space to a minimum, the air chamber D
Is at the start of the next intake stroke following the end of exhaust gas discharge, the intake port In remains open, and the compression working medium in the air chamber B has already been ignited, and the expansion pressure of this air chamber B is reduced. The air gap between the air chambers D and A is expanded by expanding the air gap between the air chambers D, and the rotating main shaft 20 is rotated. After all,
Each of the air chambers A, B, C, and D has taken one rotation and a half (180 degrees × 3) when drawing out FIG. 24A and reaching FIG. Is satisfied in each half rotation, which means that each of them has completed three strokes.

Then, by returning to FIG. 24A from FIG. 25C through (S) and (S) according to the expansion stroke of the air chamber B at that time, the rotating spindle 20 and the rotating piston 3 are returned.
0 and the swash plate 40 make two rotations (180 degrees × 4), and the air chambers A, B, C, and D complete one circulation cycle of four strokes each, and the air chambers A, B, C, and D The expansion strokes linked to each other act on each plate surface of the rotary piston 30 and are converted into the rotational force of the rotary main shaft 20, so that the air chambers A, B, C, and D
(A) through FIG. 25 (C), and again circulates between FIG. 24 (A) to repeat the respective steps of intake-compression-expansion-exhaust. The operation of the four-stroke cycle is established.

[0107]

[Torque generation principle] Like the reciprocating piston engine, the spherical rotating piston engine of the present invention has a considerably short combustion time of the working medium (in this case, an air-fuel mixture) in the combustion chamber, and roughly has a substantially constant volume of combustion. The pressure of the combustion gas corresponding to the ratio of the combustion mass is adjusted by the rotating piston 3
It acts on the arcuate surface 31 of the zero plate surface to exert a force on the rotating piston 30 itself. Then, when the rotating spindle 20 rotates,
Since the rotating piston 30 moves in the direction of the force while receiving the force of the pressure of the expanding combustion gas, this force works and is converted into mechanical energy in the form of rotation of the rotating main shaft 20. Here, the principle of torque generation in the spherical rotary piston engine of the present invention will be described with reference to FIG.

The generation of torque in the spherical rotating piston engine of the present invention can be considered in the same manner as in a conventional reciprocating piston engine. That is, the gas pressure Pg applied to the arcuate surface 31 of the rotary piston 30 including the axial column surface of the piston intermediate shaft 33
Is a circle having a diameter between two points P and Q at which each of the axes X and Y, which have moved the same distance from the spherical center O in the same direction, intersects the spherical surface G (the L axis of the rotary piston 30). In the revolution trajectory and the conical trajectory U), it can be considered separately into a cutting force Ft acting in a cutting direction of the circumference thereof and Pb acting as a journal bearing load of the rotating spindle 20 shaft neck. The center axis 25 of the pin joint joint 55 having the M axis as a connection axis corresponds to a crank pin in the reciprocating piston engine, and the hinge pins 51 at both ends (points Ka and Kb) of the K axis line are piston pins in the reciprocating piston engine. The joint between the pin joint joint 55 and the hinge joint 50 both swings by ± θ.

Also, the center axis 25 of the pin joint 55 on the M axis, the hinge pins 51 at both ends (points Ka and Kb) of the K axis, and the piston opening on the spherical surface 32 of the rotary piston 30 The center point of the window-shaped opening of the through-hole 34 (the point where the L axis intersects the spherical surface G) moves the same distance by the angle θ together with the rotation, and therefore has the same radius as the point P on the L axis. Even if it is considered that the center of the opening of the upper piston passage hole 34 corresponds to the crankpin of the reciprocating piston engine, there is no change. A point P on the X axis corresponds to a crank rotation center of the reciprocating piston engine. Therefore, the torque T of the output shaft is equal to the amount of rotation eccentricity (diameter of the orbit of the L axis, point P,
Assuming that (between Q) is e, T = Ft · e.

[0110]

[Output Calculation] Accordingly, the output Ne in the spherical rotary piston engine of the present invention is calculated by the following equation. Ne = Pme · Vh · z · i / 75 × 60 × 100 = 2 · π · T · n / 75 × 60 (PS) Ne: Shaft output Pme: Net average effective pressure Vh: Single chamber working volume (cm ³ ) n: Number of rotations of the rotating spindle (rpm) i: Number of cycles per rotation of the rotating spindle z: Number of working chambers T: Torque (kg / m) In the spherical rotating piston engine of the present invention, the rotating spindle 20 is used.
I = １ ／ (i = 1 in the case of a two-stroke cycle engine) because of one expansion stroke in two rotations of

Next, various examples of the present invention constructed using the above-described first to fourth embodiments as prototypes will be described in detail with reference to the drawings.

[0112]

First Embodiment First, a first embodiment based on the configuration of the first embodiment will be described with reference to FIGS. still,
Reference numeral 60 in the figure denotes a ring valve of a valve device Va having a ring shape. The ring valve 60 has a valve ring gear 62 and valve connection holes 66, 66. That is, in the first embodiment,
As shown in FIGS. 27 and 32, a ring valve 60 having a cylindrical shape is rotatably fitted on the outer diameter surface of the swash plate ring 43 so as to be in sliding contact with the swash plate 40. And turning on and off the working medium inflow and outflow in accordance with the volumes of the four working chambers A, B, C, and D, which repeatedly increase and decrease with the rotation, to perform a four-stroke cycle as an internal combustion piston engine. Things.

In the structure of the first embodiment, the rotating main shaft 20 in this embodiment is formed into a single straight shaft by connecting both shafts of a round bar to a shaft center 25 formed of a perforated circular plate. The rotating spindle 20 is connected to the rotating piston 30 in a relationship as shown in FIG.
When the two shaft necks are inserted into the main bearings 13 and 13 provided on the opposing walls of 0a and 10a, respectively, and the shafts are supported, the rotating main shaft 20 passes through the entire housing 10 as shown in FIGS. The rotating piston 30 and the skew plate 40 are circularly formed on two planes intersecting each other with the piston intermediate shaft 33 as a hinge axis.

In assembling the swash plate 40 and the rotary piston 30, for example, as shown in FIG.
A skewed plate body 40a having a U-shape formed by connecting two bow-shaped plates to a skewed plate ring 43 of about a semicircle and removing one side of a window frame of a window-shaped gap; Hinged pins 51, 51 are divided into two members, that is, a sloping plate retaining frame 40b made up of about the remaining semicircle, and projecting from the inner center of each skewed plate ring 43 made up of each semicircle. Form and put. Then, while inserting the piston intermediate shaft 33 from the open side of the U-shaped frame of the oblique plate body 40a, the hinge pins 51,
51 is a hinge pin receiver 5 attached to both ends of the piston intermediate shaft 33.
2 and 52, and the skew plate retaining frame 40b is fixed to the skew plate main body 40a by screws, and the rotary piston 30 and the skew plate 40 are assembled by crossing on the piston intermediate shaft 33. The skew plate body 40a and the skew plate retaining frame 4
The assembly with Ob is preferably performed by mutual melting from the viewpoint of strength and rigidity.

Further, as shown in FIGS. 27, 29, 31, and 32, the bottom wall surface of the raceway gap 12 in this embodiment is provided outside the ring valve 60 of the valve device Va fitted externally on the concentric circle of the inclined plate ring 43. Since the inner peripheral surface of the swash plate housing 10b is formed on a rotating surface having an inner diameter length slightly exceeding the diameter, the bottom wall surface of the raceway gap 12, the inner and outer peripheral surfaces of the ring valve 60, and the swash plate ring 43 Are placed on concentric circles of the same axis (Y-axis). In this case, the ring valve 60 is
The inner surface of the inner and outer circumferences of the inner diameter surface fitted to the outer peripheral surface of the outer circumferential surface and the outer diameter surface fitted to the bottom wall surface of the raceway 12 is a cylinder formed on a rotating surface slidably slidable therebetween. As shown in FIGS. 28 and 29, the valve ring gear 62 whose one side circumference is formed by cutting the bevel gear, and the valve connection hole 66 of a groove-shaped hole penetrating from the inner peripheral surface to the outer peripheral surface. , 66.

As a valve gear in this valve gear Va, as shown in FIGS. 27 and 28, a valve gear 27 of an external gear is attached to the neck of the rotating main shaft 20, and the valve gear 2 is also used.
7 and the valve ring gear 62 have a pitch circle diameter ratio of 1: 2, and the ring valve 60 is driven at a half speed of the rotation of the rotary main shaft 20 and the skew plate 40. In this case, the valve is operated. Gear 2
7 directly meshes with the valve ring gear 62, or FIG.
As shown in FIGS. 7 to 29, intermediate gears 54, 54 of an even number of external gears meshing with each other are interposed between the valve gear 27 and the valve ring gear 62 and mesh in series.
Alternatively, although not shown, the valve gear 2 mounted on the rotary spindle 20
7, two large and small external cogwheels coaxially integrated with each other by engraving the periphery of the edge of the skewed plate ring 43 on the skewed plate ring gear 48 of the bevel gear and supported by the fixed wall of the housing 10. And the large and small intermediate gears 54 are connected to the swash plate ring gear 4.
8 and the valve ring gear 62 are meshed with each other.

The working medium outflow / inflow holes are shown in FIGS.
As shown in FIG. 2, the oblique plate 4 with which the inner and outer surfaces of the ring valve 60 contact
0 and the wall of the housing 10, the swash plate 40 is formed as a through hole that communicates the inside and the outside with the swash plate passage holes 49, 4.
9, 49, 49 and housing flow passage holes 15, 15 are formed in the wall of the housing 10, and the two sets of flow passage holes are joined together with the rotation of the ring valve 60 interposed between the flow passage holes. And shut off. The inclined plate channel holes 49, 49, 49,
Reference numeral 49 denotes an air chamber-side opening opening in each of the arcuate surfaces 41 of the swash plate 40 facing the air chambers A, B, C, and D, and each of the air chamber-side openings is shown in FIGS. As shown in the figure, there are outer ports 9b, 9b, 9b, 9b which are separately communicated and opened at equal intervals on the same rotation circumference of the outer diameter surface of the inclined plate ring 43.

As shown in FIGS. 28, 31, and 32, the annular valve 60 is provided with two groove-shaped holes extending in series and having a length of approximately 1/4 of the circumference of the valve cylinder itself. The valve connection holes 66 penetrating from the inner surface to the outer surface of the valve.
However, two streaks of the valve connection holes 66, 66 have inward openings 6a, 6a opened in the inner peripheral surface of the valve cylinder on the outer circumference 9b of the outer periphery 9b of each of the oblique plate passage holes 49, and each of them has an opening. It communicates with the outward ports 6b, 6b that open on the external surfaces of the rotating cylinders that do not compete with each other on the valve cylinder. And the outward port 6b,
On the inner wall surface of the housing 10 on the two rotating circles where the opening 6b is opened, the inner ports 5a,
5a are open, each of which is a groove-shaped hole separately communicating with the outer wall surface of the housing 10, one of two circumferences of which is an intake hole In, and the other circumference is an exhaust hole Ex. is there.

Each of the housing flow passage holes 15, 15 is always connected to its own valve connection holes 66, 66, regardless of the rotational angle position of the ring valve 60. It is not necessary that the hole is a groove-shaped hole as long as the hole is always open, and as shown in FIG. 31, a hole formed on the same circumference may be continuous, and the continuous length of the continuous hole is also given to each other. If it is always connected to the connecting hole 66, it is free with the shape. Similarly, if the required circumferential length is satisfied in the valve connection holes 66, 66, the rotation is not limited to the groove-shaped hole, and the rotation circumference where the outward ports 6b, 6b are opened is also the outer circumference of the ring valve 60 cylinder. The circumference may be any one of a surface and a side surface.

The igniters Ig and Ig are inserted into the wall of the housing 10 looking into the combustion chamber having a void volume corresponding to the piston position at the top dead center. The housing 10 is located at a position where the main shaft 20 is closest to the housing 10, and is located on a plane passing through the axes of both the rotary main shaft 20 and the swash plate 40. Also, as shown in FIG. 27, they are inserted into at least two positions on the wall of the housing 10 facing each other, and one of them acts on the two air chambers A and B with the swash plate 40 as a boundary on both sides. The other is air chamber C, D
It acts on the side.

The operation and progress of each of the intake, compression, expansion, and exhaust strokes in this embodiment configured as described above will be described below.

FIG. 30 shows that the air chambers A,
FIG. 31 shows the swash plate flow passage holes 49, 49, 49, 49 rising from the respective arcuate surfaces 41 facing B, C, and D and each opening on the same rotation circle on the outer peripheral surface. The positional relationship between the swash plate flow passage hole 49, the valve connection holes 66, 66, and the housing flow passage holes 15, 15 and the shape of each hole are shown.
FIG. 32 shows the positional relationship between each of the oblique plate passage holes 49 inside and the outside of the housing passage holes 15 with respect to the ring valve 60 based on FIG. 31. As described above, the swash plate 40 rotates in the same direction as the rotation direction of the swash plate 40 at half the rotation speed of the skewing plate 40, and rotates clockwise in FIG. In FIG. 33, reference numeral A indicates the air chamber A and also indicates the inclined plate passage hole 49 communicating with the air chamber A, and reference numerals B, C, and D also indicate the air chambers B, C, and D. Each of the oblique plate passage holes 49 communicating with each of the air chambers B, C, and D is shown.
The side shows the operation on the intake side in the air chambers A, B, C, and D, and each (b) side shows the operation on the exhaust side.

In FIGS. 33 (a) and 33 (b),
The oblique plate passage hole A has an outer opening 9b that has been connected to the exhaust side valve connection hole 66 shown in FIG.
Is located at a rotational angle that is interchangeable with the intake-side valve connection hole 66 shown in FIG. 7, and the skewed plate passage hole B follows the skewed plate passage hole A, and the exhaust-side valve connection shown in FIG. Since the air chamber A at this time is the position immediately before joining with the hole 66, the air chamber A at this time starts the intake stroke when the air chamber space contracted to the minimum, and the air chamber B is at the position just before the air chamber space where the expansion is maximum enters the exhaust stroke. is there. Further, the oblique plate passage holes C and D are closed without contact with any of the intake and exhaust valve connecting holes 66 and 66, and the air chamber C is in the position where the working medium is ignited, so that the expansion stroke starts. The air chamber D is at the end of the intake stroke in which the air chamber space is maximally expanded since the swash plate passage hole D has been joined to the intake side valve connecting hole 66.

The housing flow passage holes 15, 15 formed on the two circumferences are joined to the leading sides of the two valve connecting holes 66, 66 (the leading side is an intake hole and the trailing side is an exhaust hole). The circumferential side to be connected is the intake hole In and the circumferential side to be joined to the succeeding portion is the exhaust hole Ex. Both In and Ex communicate with any of the air chambers A, B, C, and D. From the above, the skewing plate 40 and the ring valve 60 shown in FIGS.
(B), in the meantime, the air chambers A, B, C, and D complete their non-identical strokes which do not overlap each other, and the air chambers A, B,
The C and D and the swash plate 40 make a half turn (180 degrees), and the ring valve 60 turns by a 1/4 circumference (90 degrees).

That is, in FIGS. B (a) and (b), the air chamber A terminates the connection with the valve connection hole 66 on the intake side, and the air chamber B opens at the same time as the end of the exhaust stroke. B to b
Since the air chamber A is located at the position joined to the valve connection hole 66 on the intake side shown in (a), the air chamber A expands the air chamber space to the maximum, the intake stroke ends, and the air chamber B contracts the air chamber space to the minimum. It is in a state of starting the intake stroke that has been performed. Further, the air chamber D is located immediately after ignition of the working medium that has been compressed and closed, and the air chamber C has started the connection to the exhaust-side valve connection hole 66 shown in FIG. This is the position where the air chamber space having the maximum capacity enters the exhaust stroke.

Further, each of the air chambers A, B, C, D and the swash plate 40 in FIGS. ), (B), the air chamber A is in the state of starting the expansion stroke in which the compressed air is ignited,
The air chamber B has just been joined with the valve connecting hole 66 on the intake side, so it is immediately before the start of the compression stroke. Further, the air chamber C completes the exhaust stroke and starts the intake stroke because it is at the start position of connection with the intake side valve connection hole 66 as shown in FIG. C (a), and the air chamber D finishes the expansion stroke. As shown in FIG. C (b), this is the start position of exhaust gas discharge connected to the valve connection hole 66 on the exhaust side.

From FIGS. C (a) and (b), when the air chambers A, B, C, D and the swash plate 40 further make a half turn, the ring valve 60 also turns by 90 degrees. As shown in FIG. d (b), the air chamber A which has completed the expansion stroke after reaching d (a) and (b) has the swash plate passage hole A catching up with the exhaust side valve connection hole 66 as shown in FIG. Since the air chamber C has just been released from the connection with the valve connecting hole 66, the intake stroke ends and the compression stroke starts. Further, in the air chamber B, the compressed air after the compression stroke is ignited and the expansion stroke is started, and in the air chamber D, the swash plate passage hole D is filled with the end of the exhaust stroke as shown in FIG. Then, joining with the valve connection hole 66 on the intake side is started.

Next, each of the air chambers A and D in FIGS.
B, C, D and the swash plate 40 make a half turn, and the ring valve 60
When the robot arrives at a (a) and (b) departed by rotating by 0 degrees, they have returned to the a through the b, c, and d, respectively, starting from the a. The row plate 40, the rotary piston 30, and each of the air chambers A, B, C, and D make two rotations,
This means that the ring valve 60 has made one rotation. After all, skew board 4
0 and each air chamber A, B,
Since C and D complete one stroke at a time, the swash plate 40,
Two rotations of the rotary piston 30 and one rotation of the ring valve 60 are different from each other in that the ring valve 60 communicates with the swash plate flow passage holes A, B, C, D and the housing flow passage holes 15, 15 due to the difference in rotation. The holes are opened and closed to exchange the working medium in the air chambers A, B, C, and D as appropriate, and each of the air chambers A, B, C, and D sequentially performs four strokes for each cycle.

In the first embodiment, even if the ring valve 60 which rotates at a half shaft speed is changed to a rotation speed other than 1/2, four air chambers A, B, C and D are provided for every two shaft rotations. It is possible to make each process. That is, the rotation speed of the ring valve 60 is set to, for example, 3/4, 5/6, 7/8, or the like in addition to the above-described 1/2 speed of the rotation of the rotary spindle 20 and the swash plate 40.
9/10, 11/12. . . From 1/2 speed to 1
Operate with a change within the range of less than. A valve connecting hole 66, which is a pair of two lines (an intake hole and an exhaust hole) formed in the ring valve 60 with a change in the speed of the ring valve 60,
The number of drilling groups and the length of drilling muscles of each muscle vary, and the oblique plate passage holes A, B, C, and D open on the outer peripheral surface of the oblique plate 40.
, The opening position of each shell port 9b also changes, but the rotation direction of the ring valve 60 and the swash plate 40 is the same.

Next, although not shown, the valve connecting hole 66 and the oblique plate passage holes A and B when the ring valve 60 in the first embodiment has a rotation speed other than 1/2 of the shaft speed. ,
The aspects of C, D, the valve gear and the like will be described. First 3/4
The ring valve 60 having the rotation speed has a pair of two stripes having a line length of approximately 1/8 of the circumference of the cylinder of the ring valve 60 (45 degrees of the central angle of the ring valve 60). A pair of valve connecting holes (66, 66) × 2 are provided at positions facing the cylinder of the ring valve 60, and in this case, the outer openings 9b of the oblique plate passage holes A, B, C, D are formed by oblique plates. An opening is formed on the outer peripheral surface of the swash plate 40 which is not overlapped at the same position at an appropriate interval within a range of (45 degrees × 1) to (45 degrees × 7) in units of 45 degrees of the central angle of 40.

A ring valve 60 that rotates at 5/6 speed
Is approximately 1/12 of the circumference of the ring valve 60 cylinder (3
0 °), three pairs of valve connecting holes (66, 66) × 3, each pair of which is a pair of two lines connected with a line length of 0 °, are provided at equal intervals. Each outer opening 9b in B, C, and D is located at the same position at an appropriate interval within a range of (30 degrees × 1) to (30 degrees × 11) in units of 30 degrees of the central angle of the swash plate 40. The opening is formed on the outer peripheral surface of the swash plate 40 which does not overlap with the swash plate. Ring valve 6 which is further rotated at a shaft speed of 7/8
0 is approximately 1/16 of the circumference of the ring valve 60 (2
2.5 degrees). Four pairs of valve connecting holes (66, 66) .times.4 are provided at equal intervals, each pair consisting of two streaks connected at intervals of 2.5 minutes. Each of the outer ports 9b of B, C, and D has an appropriate angle within a range of (22.5 degrees × 1) to (22.5 degrees × 15) in units of 22.5 degrees of the central angle of the inclined plate 40. Openings are formed on the outer peripheral surface of the swash plate 40 that do not overlap with each other at intervals.

In addition, the 9/10 speed ring valve 60 includes:
Five pairs of valve connecting holes (66, 6) are formed by connecting two streaks, each of which is approximately 1/20 circumferential length (18 degrees) of the ring valve 60 circumference.
6) × 5 are provided at equal intervals, and the oblique plate passage holes A,
The oblique plates 9B of B, C, and D are not overlapped at intervals within a range of (18 degrees × 1) to (18 degrees × 19) in units of 18 degrees of the central angle of the oblique plate 40. An opening is provided on the outer peripheral surface 40. The 11 / 12-speed ring valve 60 has six pairs of valve connection holes (66, 66) × two streaks each having a length of about 1/24 of the circumference of the ring valve 60 (15 degrees).
6 are provided at equal intervals, and the oblique plate passage holes A, B,
Each of the outer openings 9b of C and D has a slanted plate 40 having a central angle of 15 degrees as a unit and having an appropriate interval within a range of (15 degrees × 1) to (15 degrees × 23). An opening is provided on the outer peripheral surface of the row plate 40.

When the ring valve 60 having any of the above-mentioned rotational speeds is mounted, similarly to when the above-mentioned half-speed ring valve 60 is mounted, the oblique plate passage holes A, B, C, D are formed. Each outer entrance 9b
Are opened on the same rotation circumference on the outer peripheral surface of the swash plate 40, and the valve connection holes 66, 66 are arranged so that the intake air that precedes in the rotation direction from the inner peripheral surface of the ring valve 60 on the rotation circumference of the opening 9b. A pair of holes and an exhaust hole at the rear of the housing are open on separate rotating circles on the outer surface of the ring valve 60, and housings on two rotating circles on which the valve connecting holes 66 are opened. The housing flow passage holes 15 and 15 are opened in the wall 10, and two circumferences thereof correspond to the suction and exhaust holes of the valve connection holes 66 and 66, and one of the circumferences is an intake hole In and the other is a circumference. The minute is the exhaust hole Ex.

The operations of the intake, compression, expansion, and exhaust strokes when the speed of the ring valve 60 changes are performed in the same manner as when the ring valve 60 is mounted at a half rotation speed.
And one of the four strokes in two rotations of the rotary spindle 20.
When the cycle ends, the swash plate flow path holes A,
Each of B, C, and D does not continuously join the same valve connection hole 66, 66, which is a pair of two muscles, in the next cycle. For example, installation of the ring valve 60 having a 3/4 rotation speed
Each of the oblique plate passage holes A, B, C, and D is connected to one pair of two lines of valve connection holes (66, 66) × 2 of two pairs of two lines in the previous two rotations. The exhaust stroke and the intake stroke are performed continuously, and the exhaust stroke and the intake stroke are continued in the next two revolutions by joining with the other two stripes, so that the oblique plate passage holes A,
Each of B, C, and D is a skew plate 40 and a rotation spindle 20 rotations of 2
Each rotation is alternately joined with one pair of two pairs of two streaks of valve connection holes (66, 66) × 2.

The valve operating device for the ring valve 60 corresponding to such a speed change is a ring valve 60 having a half rotational speed.
When the valve gear 27 is mounted, the valve gear 27 has a ピ ッ チ pitch circle diameter of the valve ring gear 62 (the pitch circle diameter ratio between the valve gear 27 and the valve ring gear 62 is 1: 2). Instead of the valve gear 27 having a diameter, for example, when the ring valve 60 having a 3/4 rotation speed is mounted, the valve gear 27 having a pitch circle diameter of 3/4 with respect to the valve ring gear 62 (pitch circle diameter ratio is 3: 4). Is mounted on the rotating main shaft 20, the following configuration is the same as when the above-described half-rotation speed ring valve 60 is mounted.
And the valve ring gear 62 are directly meshed with each other, or they are serially meshed with an intermediate number of intermediate gears 54, 54 of an even number of external gears meshing with each other. in addition,
5/6 when the ring valve 60 having the 5/6 rotation speed is mounted.
If the valve gear 27 having a pitch circle diameter is mounted, and the valve gear 27 having a 7/8 pitch circle diameter is mounted when the ring valve 60 having a 7/8 rotation speed is mounted, the following structure and operation are ignited in any case. Ingredient I
This is exactly the same as the case of mounting the ring valve 60 at a 1/2 rotation speed, including the insertion of g.

[0136]

Embodiment 2 Embodiment 2 shown in FIGS. 34 to 46 has substantially the same configuration and operation as Embodiment 1 described above. The purpose of the present invention is to form and attach a flow path hole through which a working medium to be bored flows in and out.

FIG. 34 shows the assembling of the components in the second embodiment, similarly to FIG. 27 showing the first embodiment, and FIG. 35 shows the ring valve 6 attached to the second embodiment.
36 and FIG. 36 show the disassembly of the entire second embodiment. In the second embodiment, as shown in FIG. 37 to FIG. , B are open on the same rotation circumference of the outer diameter surface of the swash plate 40, and the outer openings 9b, 9 of the swash plate flow holes C, D are opened.
Two of b also open on the same rotation circumference different from the oblique plate passage holes A and B. Also, two connecting lines (66, 66) of two continuous lines are provided on two circumferences of the ring valve 60 on the same rotation circumference as the opening circumferences of the oblique plate flow path holes A, B and C, D. ) ×
2 are also formed in each of two circumferences of the wall of the housing 10 inscribed in the valve connection holes (66, 66) × 2. , 15) × 2.

After all, the two opening circumferences of the oblique plate flow path holes A, B and C, D, the two opening circumferences of the valve connection holes (66, 66) × 2, and the housing flow path hole ( 15,15) × 2
Are configured so that three sets of the two opening circumferences overlap on a vertical plane, and the outer openings 9b, 9b of the oblique plate passage holes A and B or C and D are connected to the piston intermediate shaft 33. Are open at a right angle with the center angle of the swash plate 40, and two connecting lines (66, 66) × 2 have the same circumference in the half of the cylinder of the ring valve 60. About 1/4 in circumference
In each circumference, the leading side of the rotation in each circumference is bored as an intake hole In, and the lag side is bored as an exhaust hole Ex.
The igniters Ig and Ig are inserted into at least two places on the wall of the housing 10 looking into the combustion chamber having a void volume corresponding to the piston position at the top dead center, as in the configuration in the first embodiment, and shown in FIG. Thus, one acts on the two air chambers A and B, and the other acts on the air chambers C and D.

In FIG. 39, the swash plate flow path hole A is now at a position separated from contact with the exhaust side valve connection hole 66 and attached to the intake side valve connection hole 66.
When the swash plate 40 and the ring valve 60 are rotated in the direction of the arrow, the ring gear is connected to the ring valve. 60 rotates in the same direction as the swash plate 40 at half the rotation speed of the swash plate 40 rotation.
Valve connection hole 6 where B, C and D are slower than their own rotation speed
Chase and overtake 6,66 to overtake and repeat it constantly.

In this case, the continuous hole on the left side in the figure is the intake hole In on the air chamber A, B side of the housing flow path hole 15 (exhaust hole Ex on the air chamber C, D side). The chamber A is located at the position where the intake stroke starts, and the oblique plate passage hole B follows the valve connection hole 66 on the exhaust side, and the housing passage hole 15 on the valve connection hole 66 also has the air chambers A and B. Side exhaust hole Ex (the air chambers C and D sides are intake holes In).
The air chamber B is at a position where the exhaust stroke starts. The air chamber C is a rotation angle position immediately after the outer peripheral opening 9b of the oblique plate passage hole C is closed by the inner peripheral surface of the annular valve 60 and the working medium is ignited. This is the start position of the compression stroke out of the connection with the valve connecting hole 66 on the side.

FIG. 37 shows the oblique plate passage holes A, B, C, and D which open on the two rotating circles on the outer diameter surface of the oblique plate 40. Opening oblique plate passage holes A and B
The outer openings 9b, 9b of the oblique plate passage holes C, D on the other circumference are shown by solid lines, while the outer openings 9b, 9b of the other are shown by broken lines in FIG.
Reference numerals 8 and 39 denote skewed plate passage holes A, B, C and D, valve connection holes (66, 66) × 2, and housing passage holes (15, 1).
5) The position and shape of × 2 are shown, and these three are configured to overlap on two planes that can be joined. And FIG.
40a (a) and (b) show the oblique plate passage holes A and B,
C, D, the valve connection hole (66, 66) × 2 and the housing flow passage hole (15, 15) × 2 are located at the same position. Each of (a) in FIGS. 40a, b, c, and d is Each stroke on the air chambers A and B side, and each (b) shows the operation of each stroke on the air chambers C and D side.

Each of the air chambers A, B, C,
The operation of D will now be described with reference to FIG.
Is in contact with the connecting portion of the valve connecting holes 66, 66. If the swash plate 40 and the ring valve 60 rotate clockwise in the direction of the arrow, the preceding valve is opened. Since the connection hole 66 communicates with the intake hole In of the housing flow passage hole 15, the air chamber A starts the intake stroke, the air chamber B completes the expansion stroke, and the oblique plate flow passage hole B is connected to the subsequent valve connection hole 66.
It is in a state of entering the exhaust stroke connected to the. And figure a
In the air chamber C in (b), the working medium is ignited while the valve connection holes 66 and 66 of the intake and exhaust holes In and Ex are not joined and closed, and the expansion stroke is started. The air chamber space which has been expanded to the maximum by passing the valve connection hole 66 on the side is located at the rotational angle at which the compression stroke starts.

At this time, since the ring valve 60 rotates at the half speed in the same direction as the rotation direction of the swash plate 40, FIG.
When the skew plate 40 in (b) and (b) rotates by 180 degrees, the ring valve 60 rotates by 90 degrees, and as shown in FIG. B (a), the air chamber A is opened from the valve connection hole 66 on the intake side. The compression stroke is started simultaneously with the end of the intake stroke due to the disconnection, and the air chamber B is located in the middle of the two continuous valve connecting holes 66, 66, and starts the intake stroke at the end of the exhaust stroke.
As shown in (b), the air chamber C that has completed the expansion stroke starts the exhaust stroke with the outer opening 9b of the oblique plate passage hole C following the exhaust-side valve connection hole 66, and the air chamber D continues. Thus, there is no connection with the valve connection holes 66, 66, and it is at the start of the expansion stroke in which the compressed air of the working medium after the compression stroke is ignited.

Further, if the swash plate 40 is rotated by 180 degrees and the ring valve 60 is rotated by one stroke of 90 degrees in FIGS. B (a) and (b), as shown in FIG. The chamber A is at the position where the expansion stroke starts, the air chamber B is at the position where the compression stroke starts, the air chamber C shown in FIG. C (b) starts the intake stroke, and the air chamber D starts the exhaust stroke. I do. And furthermore, FIG.
If the skewing plate 40 in (a) and (b) rotates in the same direction by 180 degrees and the ring valve 60 in the same direction by 90 degrees, FIG.
The air chamber A shown in (a) completes the expansion stroke and the exhaust stroke, and the air chamber B which has completed the compression stroke starts the expansion stroke by igniting the working medium, and the air chamber shown in FIG. C is the compression stroke after the intake stroke, and the air chamber D finishes the exhaust stroke and starts the intake stroke.

In FIG. 40, when the cylinder circumference of the ring valve 60 is divided into four equal parts in order to obtain four strokes for one cycle per rotation of the ring valve 60, each stroke has a quarter circumference length. Each has a rotation angle corresponding to a right angle. That is, approximately 1 /
Assuming that the compression stroke and the expansion stroke are the remaining circumferences that are closed by providing a groove-shaped hole having a length of four circumferences, the ring valve 60 has two rotation circumferences as described above. Two connected valve connecting holes (66, 66) × 2 are formed, and one of the rotating circumferences is connected to the swash plate flow passage holes A and B, and the other is the skew plate flow. Although it is on the connecting side of the passage holes C and D, the intake stroke is started simultaneously with the end of the exhaust stroke in each of the air chambers A, B, C and D, and the swash plate passage holes A, B,
C and D are connected to the housing flow passage holes 15 and 15 via the valve connection holes 66 and 66 so as to satisfy the circumferential lengths of the suction and exhaust strokes.

In FIG. 40, the oblique plate passage holes A,
B, C, and D are equivalent to one stroke of a semicircular circumference (180 degrees)
When the valve connection hole 66 is rotated by one minute,
0 degree), and if any of the air chambers A, B, C, and D performs an intake stroke or an exhaust stroke at that time, the valve connection hole 66 also matches the intake stroke or the exhaust stroke. It is connected to one of the housing flow passage holes 15 of the suction and exhaust holes In and Ex. In addition, the housing flow path hole 1 provided on the same circumference
5, 15 each have two chambers A, B (or chambers C,
D) is shared, so that the semicircular length of the valve connection holes 66, 66 has approximately 1/4 of the circumference of the inner surface of the housing 10 corresponding to the rotation speed of 1/2, and one of them has one circumference. Exhaust hole Ex
And the other is an intake hole In.

In the second embodiment, as in the first embodiment, even if the rotation speed of the ring valve 60 is changed to a value other than 1/2 with respect to the rotation speed of the swash plate 40, each of the air chambers A, B ,
It is possible to cause C and D to repeat the four steps constituting the cycle. That is, assuming that the rotation speed of the swash plate 40 is 1, the rotation speed of the ring valve 60 is 3/4, 5/6, 7 /
8, 9/10, 11/12. . . Skew board 4
The speed of the ring valve 60 can be changed within a range of 1/2 to less than 1 with respect to 1 of 0 rotation.

In this case, similar to the configuration of the first embodiment,
In the oblique plate passage holes A, B, C, and D, the opening interval between the two outer openings 9b, 9b that open on the same circumference, the valve connection hole 66
, The length and number of muscles to be bored in the same circumference and the drilling position, and the circumferential length of the bore in the same circumference in the housing flow path hole 15 are all changed under certain conditions. When the ring valve 60 is mounted at any rotational speed, A,
The two sets of B, C, and D open on separate rotating circles on the outer peripheral surface of the swash plate 40, and the housing flow path hole 15 is provided with two lines facing each of the two circles. Groove-shaped holes shorter than a semicircular length on each of the left and right sides around a plane passing through the rotation axes of both the rotating main shaft 20 and the ring valve 60, or less than or equal to the semicircular length One hole is formed as an intake hole In and the other hole is formed as an exhaust hole Ex in the range of the ignition device Ig.
It is inserted into two places on the wall of the housing 10 looking into the combustion chamber on the D side.

In this case, the valve gear 27 has a pitch circle diameter of 1/2 when the valve gear 27 is mounted on the valve ring gear 62 when the ring valve 60 having the above 1/2 rotation speed is mounted. Instead of the ピ ッ チ pitch circle diameter, the 3/4 rotation speed ring valve 60 has a 3/4 pitch circle diameter, and the 5/6 rotation speed ring valve 60 has a 5/6 pitch diameter, 7/8 rotation speed ring. In the valve 60, the valve gear 27 having a ／ pitch circular diameter is attached, and the valve ring gear 62 and the valve gear 27 are directly meshed in the same manner as in the configuration of the first embodiment.
The intermediate gears 54, 54 are indirectly meshed with each other as a relay, and the ring valve 60 is rotated in the same direction as the rotation direction of the rotating main shaft 20 and the skew plate 40. Next, this embodiment 2
In the case where the ring valve 60 has a rotation speed other than １ ／ of the shaft speed, the valve connection hole 66 and the oblique plate passage holes A, B, C, D, etc., and the respective air chambers A, B , C and D will be described.

First, as shown in FIG. 41, the ring valve 60 which rotates at a 3/4 speed of the swash plate 40 is made to match the circumference of the opening of the swash plate flow passage holes A, B and C, D. Two sets of valve connection holes (two pairs of grooved holes each having a length of about 1/8 of the circumference) are opened in symmetrical positions on each of the two rotation circumferences in the ring valve 60 as a pair. 66, 66) × 2
In FIG. 42 showing the progress of the four strokes at the time when (66, 66) × 2 are drilled, when the swash plate 40 makes a half turn corresponding to one stroke, the ring valve 60 is rotated by 3/4 turn. Rotate a certain 3/8 circle (135 degrees). Further, in this case, the two outer ports 9b, 9b of the oblique plate passage holes A, B and C, D which are provided to each other have a center approximately 3/8 of a circle around the piston intermediate shaft 33. An opening is formed on the outer diameter surface of the inclined plate 40 separated by a length (135 degrees), and the housing passage hole (1
5,5) × 2, the valve connection holes (66,6)
6) On the wall of the housing 10 on the rotation circle of the two openings in which the opening 2 and the opening 66 (66, 66) × 2 are opened, a substantially ／ circumferential length of the inner circumference of the housing 10 (at the central angle of the housing 10). 135 °) are provided facing each other.

As a result, the progress of each stroke in FIG. 42 is similar to that in FIG. 40 in which the half-speed ring valve 60 is mounted, as shown in FIG.
The air chamber A of (a) performs an intake stroke, the air chamber B performs an exhaust stroke, the air chamber C of FIG. A (b) performs an expansion stroke, and the air chamber D performs a compression stroke. Then, in FIG. B (a), the air chamber A is in the compression stroke,
The air chamber B performs an intake stroke, the air chamber C of FIG. B (b) performs an exhaust stroke, the air chamber D performs an expansion stroke, and the air chamber A of FIG. The air chamber C of c (b) performs an intake stroke, the air chamber D performs an exhaust stroke, the air chamber A in the following FIG. d (a) performs an exhaust stroke, the air chamber B expands, and the air in FIG. The chamber C performs the compression stroke, and the air chamber D performs the intake stroke. In each of the figures, the position is immediately after the start of the stroke.

Next, in the ring valve 60 which rotates at the 5/6 speed of the swash plate 40, as shown in FIG. 43, each of the two circumferences of the ring valve 60 cylinder has a substantially 1/12 circumferential length. Three sets of valve connection holes (66, 66) × 3, (66,66) × 3 are formed at equal intervals with two pairs of grooved holes forming a pair. Further, as shown in FIG. 44, each air chamber A, B,
In the strokes C and D, the air chamber A in FIG. A (a) is an intake stroke, the air chamber B is an exhaust stroke, the air chamber C in FIG. A (b) is an expansion stroke, and the air chamber D is a compression stroke. However, the operation is shown in FIG.
A stroke similar to that of the ring valve 60 of 3/4 speed shown in FIG. The two are opened with the piston intermediate shaft 33 interposed therebetween, with the center of each being separated by approximately 5/12 circumferential length (150 degrees).

As shown in FIG. 45, the annular valve 60 having a 7/8 speed with respect to the rotation of the swash plate 40 has a groove-like hole having a substantially 1/16 circumferential length on each of two circumferences. 2 in a row
Four pairs of valve connection holes with one pair of streaks (66, 66)
× 4, (66,66) × 4 are bored, but the outer ports 9b, 9b of the two oblique plate passage holes A, B (or C, D) are also centered on each other by 7/16 circumference. Open on the same circumference separated by a distance. Each stroke of the air chambers A, B, C, and D in the ring valve 60 having the ／ rotation speed is, as shown in FIG.
46a (a), the air chamber A in FIG. 46A (a) is an intake stroke, the air chamber B is an exhaust stroke, and the air in FIG. The chamber C sequentially proceeds as an expansion stroke and the air chamber D as a compression stroke. Or 7
When the ring valve 60 is mounted at a speed higher than the / 8 rotation speed but slower than the swash plate 40, the outer openings 9b of the two swash plate flow passage holes A and B (or C and D) opened on the same circumference. , 9b is further increased, the length of a single muscle of the valve connecting hole 66 is shortened, and the pair of two muscles is increased to four or more.

[0154]

Third Embodiment Next, a third embodiment based on the configuration of the second embodiment will be described with reference to FIGS. Assuming that the element composition and the formation of the working chamber Fu in the first and second embodiments are spherical, the third embodiment has a hemispherical configuration. Connection between the rotating piston 30 and the swash plate 40, and the valve device V
a and the mounting and operation of the valve gear and the like are described in the first embodiment,
This is similar to the case of 2.

That is, the third embodiment is different from the second embodiment shown in FIG. 11 in that the entire housing 10 is divided into two by one cut plane aa parallel to the S-circle surface, and one of the cut surfaces is a concave surface formed of a circular sphere. A rotating piston housing 10a is formed on the inner wall surface 11 and slidably encloses the spherical surface 32 of the rotating piston 30. The other is a raceway space 12 having a concave space.
When the skew plate housing 10b for rotatably holding the skew plate 40 is used, the rotating piston 30 is a substantially semi-circular plate in which a piston intermediate shaft 33 is combined with a semi-circular plate.
0 designates only one plate surface of the circular plate as two arcuate surfaces 41, 41.
, And the rotating piston 30 and the side surface of the working chamber of the swash plate 40 are arranged on the same side, and the arcuate surfaces 31 and 41 face each other.

Therefore, two air chambers A, B or C, D are formed in the housing 10, and one of the main bearings 13, 13 is provided on the wall of the rotary piston housing 10a, and the other is provided on the oblique plate housing 10b. The swash plate 40 is provided on the wall, and the swash plate 40 has a swash plate through-shaft hole 44 opened at the center thereof.
The rotary main shaft 20, which is connected to the main shaft 4 and has the through shaft holes 34, 44 loosely inserted therein, is supported by inserting the main bearings 13, 13 on both opposite walls of the housing 10. In addition, the ring valve 6 shown in FIG.
0 is also similar to the ring valve 60 in the first and second embodiments.
The swash plate 40 is provided so as to be rotatable on a concentric circle of the swash plate 40, having an inner diameter surface which is in sliding contact with the outer diameter surface and an outer diameter surface which is in sliding contact with the inner wall surface of the swash plate housing 10b, 47, the valve gear 27 and the valve ring gear 62 mesh with each other to rotate the ring valve 60 in the same direction of the rotary main shaft 20 as shown in FIG.

The working fluid inlet / outlet in this embodiment is:
Swash plate flow passage holes A, B (or C, D), and ring valves 60 opened on the outer circumference of outer ports 9b, 9b of the swash plate flow passage holes A, B (or C, D). Valve connecting holes 66, 66
And housing flow passage holes 15, 15 opened in the inner wall surface of the housing 10 on the outer circumference of the valve connection holes 66, 66 on the outer circumference of rotation. The operation of the four strokes in the articulated relationship corresponds to two air chambers of only the air chambers A and B (or C and D) in the first embodiment or the air chambers A and B (or C and D) of the second embodiment. This is the same as the suction and exhaust action for one circumference on one side.

[0158]

Fourth Embodiment In a fourth embodiment shown in FIG. 50 based on the structure of the second embodiment, a semi-circular rotating piston 30 is arranged at a pivot point of the rotating main shaft 20, and the skew plate 40 is Since either one of the two plate surfaces is configured as a surface on which the working chambers Fu and Fu are formed, it is constituted by two air chambers A and B (or C and D). Same as Example 3, except that the rotary spindle 20 and the swash plate 40 are structurally different.

In other words, the rotary spindle 20 is limited to only one side in which the round bar in the shaft center pivot 25 is mounted on the shaft, and the swash plate 40 is not provided with the swash plate through-hole 44. A handle-shaped skewed plate shaft 46 having a round bar fixed to the center portion of the outer sliding contact surface 45 is opposite to the shaft of the rotary spindle 20 at the spherical axis O of the rotary spindle 20 and the housing 10 on the X axis. It is arranged on the Y-axis that intersects at an angle θ. A main bearing 13 and a skew plate bearing 14 are provided on the wall of one rotating piston housing 10a and the skew plate bearing 14 on the other skew plate housing 10b.
When the shaft and neck of the rotating spindle 20 and the swash plate shaft 46 applied to each of the shafts 3 and 14 are inserted, a fixed rotating axis is given to the rotating spindle 20 and the skew plate 40, and the rotation in the same direction is enabled. At the same time, the rotating piston 30 that is restrained and supported in two directions by the rotating main shaft 20 and the swash plate 40 can also rotate and revolve on the conical locus U.

The valve device Va in the fourth embodiment is
A ring valve 60 similar to the configuration in the third embodiment can be mounted. However, in this case, in which the skew plate 40 is supported by the skew plate shaft 46, as shown in FIG. A plate valve 61 made of a plate-like or concave circular plate is assembled on the side of the outer sliding contact surface 45. If a valve plate bearing 64 made of a circular hole is provided in the center of the plate valve 61 and the swash plate shaft 46 is fitted therein, the plate valve 61 can be mounted on the side wall of the swash plate housing 10b and the outer periphery of the swash plate 40. The swash plate 40 is rotatably slidably fitted with the sliding contact surface 45 and is supported with a rotation axis of the same orientation as the skewing plate 40. The plate valve 61 is provided with a valve ring gear 62 of a bevel gear attached to the periphery of the rim and the skew plate shaft 4.
6 or driven by the valve gear 27 comprising an external gear mounted on the shaft and neck of the rotary spindle 20 shown in FIG.

On the other hand, although not shown, the inlet and outlet holes of the working medium in this embodiment are provided with outer openings 9b, 9b, which are opened from the respective arcuate surfaces 41, 41 of the inclined plate 40 to the outer sliding contact surface 45.
Oblique plate channel holes A, B (or C, D) communicating with 9b;
Inward openings 6a, 6a opened on the plate surface of the plate valve 61 on the rotation circumference overlapping with the opening rotation circumferences of the outer openings 9b, 9b, open outward on the plate surface on the wall side of the housing 10 through the plate valve 61. 6b, a valve connecting hole 6 of a grooved hole communicating with 6b
6, 66, and the valve connecting holes 66, 66, and the housing flow passage hole 1 that opens the inner ports 5a, 5a in the inner wall surface of the housing 10 on the circumference of the opening, and communicates with the outer wall surface of the housing 10.
5, 15 are drilled. Hereinafter, the connection relationship in each stroke of the oblique plate passage holes A, B (or C, D), the valve connection holes 66, 66, and the housing passage holes 15, 15 in mounting the plate valve 61 will be described. The operation of the first and second embodiments is exactly the same as that of the first and second embodiments as long as one circumference is constituted by only the two air chambers A and B (or C and D) in the first and second embodiments. The ring valve 60 in the plate valve 61
Is replaced by

It should be noted that the above Examples 3 and 4 correspond to Embodiment 2 described above.
The above configuration and operation are based on the above. However, the components of the hemisphere in Examples 3 and 4 are set to one set, and another set that is referred to as the component of the hemisphere is configured to be two sets. If the two sets of hemispheres are linked together, the composition of the hemispheres in Examples 3 and 4 can be used to form a circular spherical capacity composed of the two sets. Next, various examples based on the fourth embodiment will be described.

[0163]

Fifth Embodiment First, as shown in FIG. 52, in the fifth embodiment, the two oblique plate housings 10b, 10b having the cylindrical axes on the same line are united, and the concave inner walls 11 on both sides thereof. , 11 facing rotating piston housing 10
a, a housing 10 in which the whole is integrated by disposing
Two sets of the rotating pistons 30, 30, the skew plates 40, 40, and the rotating main shafts 20, 20 are symmetrically arranged in the inside.

Among them, the two sets of skewing plates 40, 40 installed in the center of the housing 10 are connected to the outer sliding surfaces 4 of each other.
5 and 45 are connected on the same line to form the same circular plate, or formed into a circular body, and when one side of two sets of internal elements on both sides rotates, the other side is formed by the coaxially integrated skewing plate 40. The side also rotates. The semi-circular rotating piston 3 in this case
0, 30 are assembled with the piston intermediate shafts 33, 33 toward the center of the housing 10 and the spherical arc surfaces 32, 32 facing outward, respectively.
Each of the main bearings 13, 13 is supported by bearing a shaft column on only one side to 5, 25, but none of them penetrates the swash plate 40.

In addition, although not shown, a ring valve 60 is installed on a concentric circle of the swash plate 40.
0 has a valve ring gear 62 of a bevel gear and a valve connecting hole 66 of a groove-like hole penetrating the inner and outer surfaces, which are integrally attached to the end circumference. The outer opening 9b of the oblique plate passage hole 49 is opened on the outer peripheral surface of the oblique plate 40 on the circumference in contact with the inward opening 6a of the valve connecting hole 66, and the rotation of the valve connecting hole 66 in contact with the outward opening 6b. The inner opening 5a of the housing passage hole 15 is opened on the inner wall surface of the housing 10 on the circumference.
9, a housing passage hole 15, and a valve connecting hole 63 interposed therebetween, inflow and outflow of a working fluid in the connection and operation of each stroke in each of the air chambers A, B, C, and D, and The drive of the valve 60, the insertion of the ignition device Ig, and the like are exactly the same as the configurations and operations in the first and second embodiments.

[0166]

Sixth Embodiment A sixth embodiment shown in FIGS.
The arrangement and the assembly of the rotary pistons 30, 30 and the rotary spindles 20, 20, which are composed of two sets, are the same as in the fifth embodiment, but the connecting method of the two swash plates 40, 40 and the valve device Va In that a circular plate valve 61 is mounted in place of the cylindrical ring valve 60. That is, in the cylindrical oblique plate housing 10b in which the two are combined, the two oblique plates 40, 40 are spaced apart from each other with their outer sliding contact surfaces 45, 45 facing each other. Surface 45, 45
A swash plate connecting shaft 47 for coaxially connecting the two skewing plates 40 and 40 and also coaxially connecting the two sets of compositions in the housing 10 is fixed to the center of the skewing plate. A circular gap is formed between the plates 40, 40, and the plate valve 61 is fitted into the circular gap so as to be rotatable and slidable.

The plate valve 61 is provided with two sloping plates 4
A circular plate having two plate surfaces sandwiched between the outer sliding contact surfaces 45, 45 of each other in a rotational sliding relationship with each other and an outer diameter surface rotatably sliding on the inner wall surface of the oblique plate housing 10b, A valve ring gear 62 formed by engraving an end circumference on the external bevel gear;
And a valve plate bearing 64 having a circular hole penetrating the center. The skew plate connecting shaft 47 is fitted into the valve plate bearing 64 to support the plate valve 61 on the same axis as the skew plates 40, 40. 62 is directly and indirectly meshed with the valve gear 27 to be driven.

Although not shown, the oblique plate passage hole 49 is not shown.
Communicates with a separate outer opening 9 b opened from each arcuate surface 41 of the swash plate 40 to the outer sliding contact surface 45, and a valve connecting hole 66.
The inward opening 6a opened on both plate surfaces of the plate valve 61 on the outer circumference of the outer opening 9b communicates with the outward opening 6b opened on the outer diameter surface of the plate valve 61. The outer opening 6b is opened on the inner wall surface of the housing 10 on the rotation circumference. As a result, the formation of the working medium outflow / inflow holes and the air chambers A,
The connection and opening / closing of the working medium flow path performed with the progress of each of the steps B, C, and D is performed by replacing the ring valve 60 in the fifth embodiment with the plate valve 61.
The operation and progress of the stroke in this case are the same as those of the ring valve 60 in the first and second embodiments.

[0169]

Another Embodiment of the Sixth Embodiment (2 Valves) As another embodiment of the sixth embodiment, as shown in FIGS. 56 (a), (b) and (c), the center of the swash plate housing 10b is A housing partition 16 of a vertical wall that separates the inside from the left and right in the axial direction
Is provided, and a swash plate connecting shaft 47 is inserted through a central bearing 17 in the center of the housing partition wall 16,
The two skewing plates 40, 40 of the coaxial connection are rotatably supported. Also, swash plates 40, 40 are provided on both sides of the housing partition 16.
Although not shown, parallel gaps are formed between the housing partition 16 and each of the skewing plates 40, respectively, so that each of the gaps has a swash plate connecting shaft 47 at the center thereof.
Valves 61, 61 of circular plates having bearing holes for bearing
Is freely rotatable. In this embodiment, the components of the fourth embodiment composed of two air chambers for a hemisphere are set as one set, and the two independent sets are operably connected to each other. If the ring valves 60, 60 are externally fitted to each other in a rotationally slidable relation and actuated, the third embodiment of the two-chamber configuration is used.
Is the same as linking the two sets.

[0170]

[Embodiment 7] In the embodiment 7 shown in FIG. 57, the rotary piston housing 1 has a double wall.
0a, 10a, and skew plate housings 10b, on both sides of which are formed in raceway gaps 12, 12 of concave voids on both sides.
10b is arranged. A housing 1 corresponding to a connecting portion between the combined rotary piston housings 10a, 10a.
The center inside 0 is a concave inner wall 1 facing each other diagonally.
A housing partition 16 is provided on both sides of the housing 10 so as to separate the inside of the housing 10 on both sides. The housing partition 16 has a center of the bearing circular hole on a straight line passing through the spherical centers O, O of the concave inner walls 11, 11. Bearings 17 are penetrated, and skew plate bearings 14 having circular holes penetrating the center of the side wall of the skew plate housings 10b on both sides are also provided.

In the housing 10 thus formed, the rotating pistons 30, 30 each having a semicircular plate face each other with the arc-shaped surfaces 32, 32 sandwiching the housing partition 16 therebetween. The row plates 40, 40 are the outer sliding contact surfaces 4 of each other.
5, 45 are installed facing outward.
The skewed plate bearings 14 provided by each having a pattern-shaped skewed plate shaft 46 at the center of the outer sliding contact surface 45 are also inserted into the skewed plate bearings 14, each of which protrudes from the wall of the skewed plate housing 10 b. . on the other hand,
A rotating spindle 20 having shaft center pivots 25 fixed at both ends of a double-cut round bar is provided with a piston shaft hole in which a journal portion at a center point of a shaft is inserted into the central bearing 17 to face the housing partition 16. Each of the air chambers A, B forming the double wall and the other air chambers C, D which do not compete with each other is formed by inserting the central shafts 25 into the piston shafts 35 provided by the central shafts 25. Activate the journey.

As a result, the seventh embodiment is different from the first embodiment in that the rotating spindle 20 and the semicircular rotating piston 30 are attached to the shaft center 25 and the inclined shafts are formed with the working chambers Fu and Fu on one side. Since the components of the fourth embodiment constituted by the plate 40 are combined into one set, and the two sets are connected to each other, the connecting action of the rotating main shaft 20, the rotating piston 30, and the skew plate 40 provided to each other is provided. Is the same as the operation in the fourth embodiment,
The mounting of the valve device Va, the valve gear, and the igniter Ig is the same as that of the fourth embodiment if only one set is mounted on one side. , C,
Each step of D is for the above-described sixth embodiment configured to have two sets of valve devices Va.

[0173]

[Embodiment 8] Further, in Embodiment 8 according to the configuration of Embodiment 4, as shown in FIGS. 58 to 60, a rotating main shaft 20 having a straight shaft extends 30 and two air chambers A and B in the housing 10.
Alternatively, the hemisphere composition in the third embodiment having C and D is operated in a double configuration.

The housing 10 of this embodiment is composed of a rotating piston housing 10a, 10a in which the united swash plate housings 10b, 10b are placed inside, and the concave inner wall surfaces 11, 11 face diagonally on both sides thereof. The whole was made into one structure. In other words, the Y-axis and the Y-axis intersecting the straight line (X-axis) passing through the spherical centers O, O of the concave inner walls 11, 11 at angles θ, θ on the spherical centers O, O, respectively, are defined as central axes. Since the two raceways 12, 12 of the concave gaps formed in the two oblique plate housings 10b, 10b are obliquely opposed to each other, a central portion in the housing 10 is a housing partition 16 of a fixed wall. 16
Central bearing 17 in the center and double rotating piston housing 1
The main bearings 13 and 13 are respectively provided on the walls 0a and 10a with the X-axis passing through the housing 10 as a perforation axis.

In the housing 10 thus formed, each of the semi-circular rotary pistons 30, 30 is provided with a spherical arc surface 3.
The two slanting plates 40, 40 are assembled with the housing partition 16 obliquely sandwiched therebetween with the sides 2, 32 facing outward in the major axis direction of the housing 10. The swash plates 40, 40 are provided with swash plate through-holes 44, 44 penetrating through the central portions thereof, and connected to the piston through-holes 34, 34 provided to each other.
Both piston through-holes 34, 3 connected in a chain on the same line
4 and the two oblique plate through-holes 44, 44, the central bearing 17, and the two main bearings 13, 13, a through-hole penetrating through the housing 10 is formed. The rotating main shaft 20 is connected to the piston pivots 35, 35 on the spheres O, O provided by the two central pivots 25, 25 within the axial length, and the central axis and the left and right axial necks. Provide the central bearing 17 and the main bearings 13
And the bearing is supported.

The valve device Va according to this embodiment is different from the valve device Va shown in FIGS. 59 (a) and 59 (b) in that the two annular valves 60, 60 shown in FIGS.
The connection between the swash plate flow passage hole 49 and the housing flow passage hole 15 is turned on / off by being fitted on the concentric circle 0, but the valve operating device for the ring valves 60, 60, the ignition devices Ig, Ig, etc. are also included. In the third embodiment, the components in the third embodiment are set as one set, and the components and the functions in the two sets are the same as those in the third embodiment. It works as a double wall.

The two ring valves 60, 6 to be mounted are
The connection between 0 and the four air chambers A, B, C, and D operates and proceeds in the same manner as the combination of the four strokes performed by the four air chambers A, B, C, and D in the configuration of the second embodiment described above. . That is, in FIG. 58, when the air chamber A is located at the rotation angle at which air is supplied, the air chamber B is caused to perform an exhaust stroke, and simultaneously, the air chamber C is caused to perform an expansion stroke, and the air chamber D is allowed to perform a compression stroke. When the air chambers A and B are connected to the air chambers C and D such that
The air chamber B performs an intake stroke, the air chamber C performs an exhaust stroke, and the air chamber D performs an expansion stroke. Alternatively, although not shown, the fourth embodiment is applied to the outer sliding contact surface 45 side of each of the inclined plates 40 instead of the ring valves 60, 60.
The same four-stroke cycle occurs even if the plate valve 61 having the same configuration as that described in the above is provided and operated by providing the flow path holes In and Ex, the valve connection hole 66, and the valve operating device that function similarly.

The phase of assembling the semi-circular disc-shaped rotary piston and the swash plates 30, 40, 30, 40 into the housing 10 in the structure of the eighth embodiment changes relative to each other on the rotary main shaft 20. It is possible. Next, a description will be given of an embodiment in which the pair of the rotating piston and the skew plates 30 and 40 are regarded as one set, and the built-in phases of the two sets are changed. Of 1
The pairs operate in exactly the same way, and the two walls connected by the rotating spindle 20 rotate in the same direction and at the same speed.

[0179]

Ninth Embodiment FIG. 61 shows another embodiment of the eighth embodiment.
The ninth embodiment shown in (a), (b) and (c) is a skewed plate housing 1 in which two sets of rotating piston housings 10a, 10a are provided with raceways 12, 12 on both sides of a concave space.
0b and 10b are combined. The joint of the united rotary piston housings 10a, 10a is connected to the concave inner wall 1 of each other.
Housing partition 16 in which 1, 11 are obliquely opposed to each other.
The main bearings 13 and 13 are formed on the walls of the two oblique plate housings 10b and 10b on a straight line passing through the two ball centers O and O.
And a central bearing 17 on the housing partition 16.

In the housing 10 thus formed, both semicircular disc-shaped rotary pistons 30 and 3 are mounted on a straight shaft of a rotary main shaft 20 to which the bearings 13, 17 and 13 are fitted.
0 are spherical surfaces 32, 3 of each other with the housing partition 16 interposed therebetween.
2 and the oblique plates 40, 40 on both sides thereof face the working chamber forming surface obliquely. At this time, although not shown, the same ring valve 60 as that of the eighth embodiment described above,
60 or a plate valve 61 may be provided, and a working fluid passage, a valve train, and an igniter Ig are also provided in the same manner as in the eighth embodiment.

[0181]

Embodiment 10 As another embodiment of the above-mentioned Embodiment 8, FIG.
In Example 10 shown in FIG. 2, one of the two wall surfaces of the housing partition 16 is the concave inner wall 11 of the rotary piston housing 10a, and the other is the side wall surface of the oblique plate housing 10b. That is, in the housing 10, two sets of pairs of the rotating piston housing 10a and the swash plate housing 10b are arranged in series in one of the long axis directions of the housing 10, and both spherical centers O, O Bearing on a straight line passing through
Since the main bearings 13 and 13 are provided in the housing partition 16 through the center bearing 17 and the walls of the rotating piston housing 10a and the wall of the oblique plate housing 10b which correspond to both ends of the major axis of the housing 10, the rotating main shaft 20 penetrating them is connected to the housing. 10 Penetrates in the long axis direction.

Further, as described above, the semi-circular disc-shaped rotating piston and the swash plate 30, 40, 30, 40, which are assembled in the same direction so as to point to one side in the major axis direction of the housing 10 as described above.
In other words, the rotating piston 30 having the concave inner wall 11 as the housing partition 16 slides the spherical surface 32 against the surface of the housing partition 16, and the other rotating piston 30 places the spherical surface 32 at the end of the housing 10. The swash plate 40 to be provided slides the outer sliding contact surface 45 against the surface of the housing partition wall 16. In this embodiment, too, the working fluid passage holes In and Ex and the valve device Va, and the valve gear and the ignition device Ig are used. Are the above Examples 8 and 9.
This is the same as the mounting in the configuration described above.

[0183]

Embodiment 11 In Embodiment 8, the ring valve 6
An eleventh embodiment in which a plate valve 61 is mounted instead of 0 and 60 will be described with reference to FIG. In the eleventh embodiment, a rotary piston housing 10a, 10a having diagonally facing concave inner walls 11, 11 is disposed on both sides of a swash plate housing 10b in which both are integrated.

In this embodiment, the rotating piston housings 10a, 10a on a straight line (X-axis) passing through the two spherical centers O, O are shown.
The main bearings 13 and 13 extend through each of the opposed walls 10a, but there is no partition wall and no central bearing formed in the center of the housing 10. That is, the inclined plate housing 10 in which the two are combined
b, three step-like internal chambers having three internal surface forming axes parallel to a plane passing through both the X and Y axes and having a parallel interval divided into a central portion and both side portions thereof; Are formed, and the inner chambers on both sides thereof are defined as the raceway gaps 12, 12,
When the central portion is also formed as a circular space interposed on both sides, the stepped space of the three internal chambers and the concave inner walls 11, 11 on both sides thereof are formed.
The interior space is combined with the inner space to form the inside of the housing 10 as one continuous space.

In the housing 10 thus formed, a plate valve 61 formed in a round flat plate as shown in FIG. 64 is incorporated in the central portion (broken line portion in FIG. 63) of the three internal chambers. Skew plates 40, 4 are provided in raceway gaps 12, 12.
The rotary pistons 30, 30 having the spherical surfaces 32, 32 facing each other in the longitudinal direction of the housing 10 are opposed to each other on both sides of the circular piston.
The circular flat plate of the plate valve 61 has two plate surfaces that rotate and slide on the outer sliding contact surfaces 45 and 45 of the oblique plates 40 and 40 and an outer diameter surface that rotates and slides on the inner surface of the center of the three internal chambers. A valve through-hole 65 having a circular hole penetrating the center portion thereof; a valve ring gear 62 having an internal bevel gear attached to an end circumference of the valve through-hole 65; The valve connection hole 6 is a groove-shaped hole that communicates from the inward ports 6a, 6a opened on both plate surfaces as passages to the outward ports 6b, 6b opened on the rotating outer diameter surface.
6, 66.

As a result, the oblique plate through-holes 44 on both sides are connected to the valve through-hole 65 by providing them with the piston through-holes 34, 34, and further connected to the main bearings 1 on both sides of the housing 10.
Since the bearing holes 3 and 13 are also connected and penetrate the entire housing 10, the rotating main shaft 20 is inserted into the space penetrating the housing 10 so that the necks of both shafts are supported by the main bearings 13 and 13. Also in this embodiment, although not shown, the oblique plate passage holes 49 are not shown.
The outer opening 9b of the valve connecting hole 66 and the inward opening 6a of the valve connecting hole 66 are opened on the same rotation circumference, and the outer connecting port 6 of the valve connecting hole 66 is opened.
b and the inner opening 5a of the housing passage hole 15 are also opened on the same rotating circumference.
In the rotation process of each of the air chambers A, B, C, D
Since the opening and closing are repeated in response to the change in volume, the operation is the same as the attachment of the plate valve 61 having the configuration in the sixth embodiment described above.

The valve operating device for driving the plate valve 61 may have the same configuration as that of the sixth embodiment, but FIG.
As shown in FIG. 7, the valve ring gear 62 is attached to the end circumference of the valve shaft hole 65 of the plate valve 61, and the valve gear 27 of the external bevel gear smaller than the valve ring gear 62 is attached to the center of the rotary main shaft 20. To the plate valve 6
1 rotates in the same direction at a lower speed than the rotating main shaft 20.
The plate valve 61 and the two sloping plates 40, 40 do not have a rotation axis on the same straight line. The plate valve 61 is a circular flat plate because it is limited to a plane formed by the rotating surface.

[0188]

Embodiment 12 Based on the structure of the first embodiment, FIG.
In the twelfth embodiment, a circular plate-shaped rotary piston 30 and a skew plate 40 are paired in a spherical housing 10 except for the structure of the suction and exhaust mechanisms, and four combs are formed in the housing 10 in a spherical space. Since the chambers are formed in the shape chambers A, B, C, and D, the composition of the sphere is the same as that in the first and second embodiments.

In this embodiment, the housing 10 includes:
A rotating piston housing 10 is provided on each of both opposing sides centered on a plane passing through both the Y-axis of the raceway gap 12 and the X-axis of the main bearings 13 and 13 as passages for the working fluid.
a, 10a two housing flow passage holes 15 penetrating the wall,
The great circles of the different housings 10, 15, 15, 15 are formed, circling in the wall of the housing 10 across the central swash plate housing 10b, and having different radial lengths from the sphere O. Two ring-shaped and band-shaped gaps that pass through a plane and pass through one of the two sides of the housing flow passage holes 15, 15, 15, 15 that do not compete with each other, and cross each other in a three-dimensional manner in the form of a hook. The valve track gaps 19, 19 are formed.

The two valve raceway gaps 19 having different diameters,
19, two large and small ring valves 60, 60 with different passing lengths applied to each of them are incorporated in a freely rotatable fitting state, and each of the large and small ring valves 60 is provided along the same rotation circumference. Penetrates the inner and outer surfaces and is approximately 1/2 of its circumference
It has a valve connecting hole 66 of a groove-shaped hole having a circumferential length, and a valve ring gear 62 formed by engraving an edge circumference on a bevel gear,
The valve ring gear 62 directly meshes with and is driven by the valve gear 27 attached to the rotary spindle 20. Also, the valve connection hole 66
During the rotation of the ring valve 60.
5, when the working medium flows out or in the working chamber Fu inside, one of the two annular valves 60 is pierced into the opposing wall of the housing 10 at the inflow and outflow. The intake ports In, In on both the air chambers A, B side and the air chambers C, D side provided are opened and closed, and the other opens and closes both exhaust ports Ex, Ex.

That is, the half rotation of the rotary piston 30 and the swash plate 40 changes the air chamber gap between the air chambers A, B, C, and D to either the maximum contraction or relaxation, and the four strokes Of the two air chambers A and B in one revolution,
Alternatively, C and D correspond to the continuous opening or closing of the intake port In or the exhaust port Ex. In this case, the rotation ratio based on the pitch circle diameter of the valve gear 27 and the valve ring gears 62 is 62. :
If it is set to 1, the ring valves 60, 60 are driven at half the shaft speed of the rotary main shaft 20, so that each of the air chambers A, B, C, D completes the four strokes of one cycle.
It is sufficient that the swash plate 40 makes two rotations and the ring valves 60, 60 make one rotation. Accordingly, in each valve connection hole 66, since a quarter of the circumference of the ring valve 60 corresponds to one stroke of each of the air chambers A, B, C, and D, the two air chambers are connected. / 2 is formed in a groove-shaped hole having a circumferential length of a circumference.

Now, in FIG. 66, the intake holes In on the air chambers A and B side and the valve connection hole 66 on the intake side are at the position where the connection starts, but when the intake stroke of the air chamber A ends, the intake hole I is closed.
n is connected to the middle position of the valve connection hole 66 having a 周 circumference, and the next intake stroke is regarded as being in the air chamber B. To the muscle length of the 1/4 circumference. Further, assuming that the air chamber B makes a half turn to end the intake stroke, the valve connecting hole 66 on the intake side separates from the intake hole In on the air chambers A and B side and the intake hole In on the air chambers C and D side. The air chamber C is joined to the air chamber C for the 先行 circumferential length, which is the leading side of the 円 circumferential length, and the 後 半 circumferential length for the second half is joined to the air chamber D. Further, in FIG. 66, the exhaust holes Ex on the air chambers A and B side are 1/1/2 of the exhaust side valve connecting holes 66 having a half circumference.
It is in contact with the middle part corresponding to 4 circumferences,
That is the position where the exhaust stroke of the air chamber A ends and the air chamber B enters the exhaust stroke. Further, when the air chamber B makes a half turn from that position and operates for one stroke, the valve connection hole 6 on the exhaust side thereof is opened.
6 is connected to the exhaust holes Ex on the side of the air chambers C and D to cause the preceding air chamber C to perform an exhaust stroke, and is joined to the air chamber D at the same time.

As a result, about one circumference of each ring valve 60, a half of the circumference of the ring valve 60 is substantially the range of the length of the valve connecting hole 66, and the remaining half of the circumference of the ring valve 60 is the housing flow path. Hole 15,
Nothing is perforated around the circumference to block 15. Therefore, each valve connection hole 66 is always connected to either the intake stroke or the exhaust stroke for two air chambers, and is connected to the valve connection hole 66. The circumference corresponds to the compression stroke and the expansion stroke of each of the air chambers A, B, C, and D, and the other half corresponds to the exhaust stroke and the expansion stroke on the intake side, and corresponds to the intake stroke and the compression stroke on the exhaust side. Hereinafter, the progress of the four strokes in each of the air chambers A, B, C, and D including the insertion of the ignition device Ig is the same as the operation of the configuration in the first and second embodiments.

[0194]

Embodiment 13 A thirteenth embodiment shown in FIG. 67 is different from the twelfth embodiment in that the two-ring valve 6 mounted in a
Instead of 0 and 60, only one ring valve 60 is mounted, and the other configuration and operation are the same as those of the twelfth embodiment. That is, the valve raceway gap 19 which is provided on the housing flow passage holes 15, 15, 15, 15 passing over the two half-moon-shaped working chambers Ha, Ha has a uniform cross-sectional area and a rotating spindle 20.
And has an axis that intersects at an angle other than a right angle, and turns around the inside of the wall of the housing 10 in a belt shape. In addition, similarly to the configuration in the twelfth embodiment, the housing 10 faces each half-moon shaped working chamber Ha.
The two housing flow passage holes 15, 15 formed in the wall are:
One of them is an intake hole In, the other is an exhaust hole Ex, and two intake holes I for both half-moon working chambers Ha, Ha.
n and In are located on the leading side where the air chamber spaces of the air chambers A and B and C and D always start to expand, and the exhaust holes Ex and Ex are also the air chambers of the air chambers A and B and C and D. The space is provided at a position on the leading side where contraction always starts.

Then, a ring valve 60 is rotatably slidably assembled into the valve raceway gap 19, and as shown in FIG. Valve connecting holes 66 and 6 having long groove-like holes penetrating the inner and outer peripheral surfaces
6, a valve ring gear 62 whose edge circumference is engraved on a bevel gear
Example 1 is also provided on the shaft neck of the rotary spindle 20.
2, the valve gear 27 of an external bevel gear having a half pitch circle diameter of the valve ring gear 62 is attached and meshed with the valve ring gear 62, and the ring valve 60 is rotated.
0 is driven in the same direction at 1/2 speed. Then, with the rotation, the valve connection hole 66 opened on one circumference is joined to the two opposed intake holes In, In, and the valve connection hole 66 opened on the other circumference also has two opposed air holes. Since this embodiment is joined to the exhaust holes Ex, Ex, in this embodiment, the valve connection holes 66, 66 formed in the circumference of each of the two ring valves 60, 60 in the twelfth embodiment are connected to two circles of one ring valve 60. It is pierced around and operated.

[0196]

[Embodiments 12 and 13] Another embodiment common to Embodiments 12 and 13
As another mode of the third embodiment, a ring valve 60 with a changed rotation speed can be attached, but changing the speed of the ring valve 60 involves changing the muscle length and the number of muscles of the valve connecting hole 66.
That is, three valve connecting holes 66, 66, 66 each having a muscle length of approximately 1/6 circumference are provided at equal intervals on the same circumference of the ring valve 60, and the ring valve 60 is rotated by the rotating spindle. Embodiment 1 even when linked at a speed of 1/6 of 20
The same four-stroke cycle operates as in cases 2 and 13. In addition, the valve connecting holes 66, 66, 66, of five lines each having an approximately 1/10 circumferential length on the same circumference of the ring valve 60.
66, 66 may be arranged at equal intervals, and the ring valve 60 may be linked at a speed of 1/10 of the rotation of the rotary spindle 20;
Alternatively, four strokes are activated even when a rotation speed of 1/14 is given by giving seven stripes each having a 1/14 circumference length to the same circumference of the ring valve 60, or approximately a 1/18 circumference length. 1 of 9 muscles
At a rotational speed of 18, 11/22
The muscles may be rotated at 1/22 rotation speed, and are operable for higher speed configurations.

[0197]

Fourteenth Embodiment A fourteenth embodiment shown in FIG. 69 is different from the structure of the thirteenth embodiment in which one ring valve 60 is disposed so as to have an axis which intersects the rotary main shaft 20 at an angle other than a right angle. A ring valve 60 shown at 70 has a mounting axis orthogonal to the rotating spindle 20 and is installed horizontally with respect to the rotating spindle 20. That is, when the ring valve 60 is assembled into the valve raceway 19 orbiting in the wall of the housing 10, the ring valve 60 and the rotary main shaft 20 are on the same plane and their rotation axes are orthogonal to each other. The main shaft gears 28, 28 of external gears are attached to both ends of the cut-out portions so as to fit inside the ring valve 60 and do not penetrate outside the housing 10. The bearings are mounted on main bearings 13 and 13 provided on the shaft.

The ring valve 60 in this case also has a valve ring gear 62 formed by engraving an end circumference on a bevel gear having a pitch circle diameter twice as long as the main shaft gear 28, and two ring circumferences. Valve connection holes (66, 66) penetrating the upper and lower inner and outer peripheral surfaces through the grooved holes
The valve gear for moving the ring valve 60 includes an odd number of external gear intermediate gears 54 meshed in series with the valve ring gear 62 on the circumference of the valve ring gear 62.
(The number is one in FIG. 69).
When the coupling shaft gear 23 of the external gear that meshes with the main shaft gear 28 and meshes with the intermediate gear 54 on the rotation circumference of the shaft is mounted on a fixed wall of the housing 10 and mounted, the valve ring The gear 62 is driven by the main shaft gear 28 through meshing between the intermediate gear 54 having the double tooth width and the joint shaft gear 23.

As shown in FIG. 69, the output joint shaft 22 to which the joint shaft gear 23 is fixedly attached to the inner end of the shaft is projected outside the housing 10 as an output shaft, but the valve ring gear 62 is driven. The joint shaft gear 23 may be provided on only one of the two sides, and the other joint shaft gear 23 is formed so as to be able to mesh only with the main shaft gear 28 so that the intermediate gear 54 is not interposed. On the side to be driven, the main shaft gear 28 meshes with the joint shaft gear 23, and the joint shaft gear 23 has an intermediate gear 54 having a double tooth width.
The coaxial gear portion of the intermediate gear 54 other than the engagement with the joint shaft gear 22 meshes with the valve ring gear 62, but the pitch circle diameter ratio between the valve ring gear 62 and the main shaft gear 28 is 2: 1. The ring valve 60 is driven by the rotary spindle 20 at a half speed.

The valve connection holes (66, 66) × 2 of the ring valve 60 in this embodiment are formed such that two streaks of a groove-like hole having a substantially 1/4 circumference are formed on each of two circumferences. It is provided continuously within two circumferential lengths, and the two circumferences of two lines are arranged in parallel. Further, the housing flow passage holes 15, 15, 15,
Reference numeral 15 denotes suction and exhaust holes In,
Four pairs of holes, each paired with Ex, are formed on the same plane of the wall of the housing 10 at equal intervals spaced by a quarter circumferential length, but on another parallel plane. In addition, two pairs of four intake and exhaust holes In and Ex are formed at equal intervals, and the four holes are parallel to each other. The housing passage holes (15, 15, 15,
15) Valve track gap 19 for mounting × 2 and ring valve 60
Are mounted on the same plane.

The operation of each step in the fourteenth embodiment will be described with reference to FIG. Note that FIGS. 71a, b, c, d
In (a), the ring valve 60 and the intake and exhaust holes (I
(2, n, Ex, In, Ex) × 2 are viewed from a planar position, and each of the (b) given to them is a ring at that rotation angle. Since only the valve connection holes (66, 66) × 2 of the valve 60 are shown, each of FIGS.
(B) is given to each other to represent the same position at the same rotation angle, and in each (a), the air chamber A,
The B side and the right side are the air chambers C and D sides.

First, FIG. 71 (a) which is the starting point of each process,
In (b), the leading two valve connecting holes 6
6, 66 are located between the intake holes In and the exhaust holes Ex on the air chambers A, B side, and the valve connecting holes 66, 66 of the next two muscles are the air chambers A, B.
Is located between the exhaust hole Ex on the air chamber side and the air intake port In on the air chambers C and D sides. At this time, the movable parts shown in FIG. 71a (a) and FIG. 69 are at the same rotational angle position, but the air chamber spaces of the air chambers A and C are both contracted and have the minimum volume. On the contrary, the air chamber spaces of the air chambers B and D are both expanded and have the maximum volume.

From the above, FIG. 71 (a) and FIG.
When the air chamber A is compared with the air chambers A and B,
n, and the preceding valve connecting holes 66,
66 ends the connection with the exhaust holes Ex on the air chambers A and B, and the tip is located so as to come into contact with the intake holes In on the air chambers A and B. At the start position of the intake stroke, and at the rotation angle position where the exhaust holes Ex on the air chambers A and B are joined to the valve connection holes 66 and 66 on the succeeding side following the preceding side, the air chamber space is maximized. The air chamber B expanded at the end of the expansion stroke is located at the start of the exhaust stroke. At that time, the air chambers C and D are connected to the valve connection holes (66, 6).
6) There is no contact with × 2, the chamber is closed, the air chamber C is just after the compressed air is ignited, and the air chamber D is at the position where the compression stroke starts at the end of the intake.

From FIG. 71 (a) and (b), each of the air chambers A, B, C, and D makes a half turn, and the ring valve 60 moves to one full circle.
When the ４ circumference is rotated in the direction of the arrow, FIG.
As shown in (b), the leading side of the valve connection holes (66, 66) × 2 is between the exhaust holes Ex on the air chambers C and D and the intake holes In on the air chambers A and B, and the trailing side is the air chamber. It is located between the intake holes In on the A and B sides and the exhaust holes Ex, but between the exhaust holes Ex and the intake holes In on the air chambers C and D, and between the intake holes I on the air chambers C and D.
There is no valve connection hole (66, 66) × 2 between the air chamber A and the exhaust holes Ex on the air chambers A and B, and the suction and exhaust holes In and Ex on the air chambers C and D are both closed. In Fig. B (a), the air chambers A and C are located at the rotation angles where the air chamber space is maximized, and the air chambers B and D are both contracted to the minimum.

That is, in FIGS. B (a) and (b), the air chamber A is at the rotation angle position at which the connection with the intake port In is terminated and the compression stroke is started, and is shown behind the air chamber A. The air chamber B which is not removed is separated from the connection with the exhaust port Ex and the intake port In
Similarly, an air chamber C (not shown) on the rear side of the air chamber D is brought into the exhaust stroke by the preceding valve connection holes 66, 66 coming into contact with the exhaust holes Ex on the air chambers C and D side. D is the position of the rotation angle at which the compressed air is ignited while the intake hole In in the rotation direction is closed. In addition, the valve connecting hole (6
6, 66) × 2 leading two muscles are connected only to the air chamber A and the air chamber C, and two succeeding muscles are connected only to the air chamber B and the air chamber D. It is alternately connected to the hole In.

Further, from FIGS. B (a) and (b), each air chamber A,
In FIGS. C (a) and (b) in which B, C and D have rotated half a turn and the ring valve 60 has rotated 90 degrees, the air chambers A and D are not shown behind the air chambers B and C. The chamber A is at the ignition position after the compression stroke in which the intake hole In in the rotation direction is closed, and the chamber B is at the start of the compression stroke in which the exhaust stroke Ex in the rotation direction is closed and the intake stroke is ended. . At this time,
The two leading valve connecting holes 66, 66 are air chambers C,
After the exhaust hole Ex on the D side, the air chamber C is located at a rotation angle position that can be joined to the intake hole In. Therefore, the air chamber C that has completed the exhaust stroke starts the intake stroke at the same time as the expansion of the air chamber space. Since the exhaust hole Ex on the D side is also located at a position connected to the subsequent valve connecting holes 66, 66, the air chamber D that has completed the expansion stroke is a position where the expanded air chamber space enters the exhaust stroke.

Then, when each of the air chambers A, B, C, and D further makes a half turn (the ring valve 60 is 90 degrees), FIG.
As shown in (b), the preceding valve connecting holes 66, 66 have completed joining with the air inlets In on the air chambers C, D, and the air chambers A, B
The air chamber A, which has completed the expansion stroke, starts the exhaust stroke, since the exhaust angle Ex is located at the rotation angle position at which the exhaust hole Ex is opened.
The air chamber B (not shown) is located behind the valve connecting hole (66, 6).
6) There is no contact with × 2, and the working medium after the compression stroke is ignited to start the expansion stroke, and the air chamber C (not shown) behind the air chamber D ends the intake stroke, and the expanded air chamber space becomes When the compression stroke starts, the air chamber D is located at a position in contact with the intake port In, and the contracted air chamber space that has finished the exhaust stroke starts the intake stroke.

Then, each of the air chambers A, B, C, and D further rotates half a turn from the time of FIGS.
When the air chambers A, B, C, and D advance the respective strokes and return to the first diagrams a (a) and (b), the air chambers A, B, C
B, C, and D make two rotations throughout and the ring valve 60
That means that each chamber A, B, C,
This means that D has completed four non-overlapping steps. That is, b, c, d from FIGS. 71a (a) and (b)
Figures (a) and (b) departed after each of (a) and (b)
Is repeated as one cycle, the combustion energy at that time is continuously converted into mechanical energy to rotate the rotating spindle 20 and the rotating spindle 20.
The mounted main shaft gear 28 rotates the output joint shaft 22 via the joint shaft gear 23.

[0209]

Fifteenth Embodiment Next, a description will be given of a fifteenth embodiment shown in FIGS. 72 and 73 having a configuration based on the second or fourth embodiment. In the fifteenth embodiment, a mushroom valve 70 is mounted on the flow passage hole 49 of the swash plate 40 instead of the ring valve 60 or the plate valve 61 attached in the above embodiment. Is driven by the cam of the prime mover as a follower articulation, so that the configuration is exactly the same as in the previous embodiments except for the valve body and the valve gear.

The mushroom valve 70 shown in FIGS. 72 and 73 is incorporated in the swash plate 40 and includes a valve head 7a and a valve rod 7b, and has a valve spring 7c in the direction toward the end of the valve rod 7b. Reference numeral 71 in the drawing denotes a cam disk of a three-dimensional cam formed in an end cam shape, and is driven by a cam plate drive gear 75 attached to the rotary spindle 20 in the configuration of the embodiment shown in FIG.
The passage holes In and Ex through which the working fluid flows in and out are formed by bending the housing passage hole 15 penetrating the inside and outside of the housing 10 wall and the L-shaped bent hole 41 from the arcuate surface 41 to the outer peripheral surface of the inclined plate 40. A swash plate flow path hole 49 is provided, and these are opened and joined on the same rotating circle.

[0211]

Embodiment 1 of Embodiment 15 In the embodiment based on the structure of Embodiment 2 in Embodiment 15, as shown in FIG. 72, the mushroom valves 70, 70 are opened and closed to open and close the oblique plate passage holes 49, 49. The circular cam plate 71 is inserted into the swash plate 40 and arranged side by side on the outer sliding contact surface 45 side of the back surface of the swash plate 40. The cam disk 71 has a cam plate ring gear 73 in which a cam plate through hole 72 through which the rotary spindle 20 is inserted is opened at the center and an end circumference is cut into a bevel gear. In FIG. 20, 1/2 of the cam plate ring gear 73 is mounted on the shaft neck of the cam disk 71 side.
A cam plate drive gear 75 of an external bevel gear having a pitch circle diameter is attached and meshed with the cam plate ring gear 73, and the cam disk 71 is driven at a half speed of the rotating main shaft 20.

The cam disk 71 has two ridge-shaped protrusions (referred to as cams) having different diameters formed of concentric circles on the plate surface on the side of the skew plate 40, and corresponds to the contour curve of the cam. This is a driving joint formed by connecting an end cam having two large and small cylindrical end surfaces as sliding surfaces to a side surface of a circular plate. Each of the two cam streaks comes into contact with the end of the valve rod 7b, 7b corresponding to the bottom surface of the tappet of the mushroom valve 70, 70 provided by each, and when the cam disk 71 rotates as shown in the figure, the end of the valve rod 7b. The convex surface of the cam which is in contact with the valve acts to push up the valve stem 7b, and the valve stem 7b pushes up the valve head 7a to open the valve 70. However, if the cam does not act, the valve 70 is moved by the valve spring 7c. Closed in close contact with the valve seat.

On the other hand, the oblique plate passage holes 49, 49 communicating with the respective air chambers A, B are opened at the opposed outer peripheral surfaces of the oblique plate 40 separated from each other by 180 degrees. Holes 49, 49 The housing flow passage holes 15, 15 which are grooved holes are also opened on the wall of the housing 10 on the circumference of the opening. This housing passage hole 1
Reference numerals 5 and 15 indicate that the circumference of the groove-shaped hole corresponds to the rotating spindle 20 and the swash plate 4.
0 and a plane passing through both axes, the boundary is divided into semicircular lengths, one of which is an intake hole In and the other is an exhaust hole Ex. Continuous circular holes may be arranged in series within the range of the muscle length.

In FIG. 72, in the air chamber A in which the mushroom valve 70 is opened by shrinking the air chamber space to the minimum, the oblique plate flow path hole 49 and the intake hole In of the housing flow path hole 15 are joined. Therefore, if the air chamber A further rotates, the intake stroke starts, and the air chamber B also has the mushroom valve 70 opened and the oblique plate passage hole 4
When 9 is at a rotational angle position that can be joined to the exhaust hole Ex of the housing flow passage hole 15 and the air chamber space starts to contract, the exhaust stroke starts. As a result, as described above, since the cam disk ring gear 73 meshes with the cam plate driving gear 75 and is driven by the rotating main shaft 20, the cam disk 71 has two ridges on the plate surface of the cam disk 71. And a valve stem 7 in contact with the ridge.
The cam disk 71 is used as an original vehicle by the ends of b and 7b, and the mushroom valves 70 and 70 as followers are opened and closed with rotation. Therefore, during the exhaust stroke and the intake stroke, the mushroom valves 70, 70 are pushed up to open the swash plate flow passage holes 49, 49. , 70 are closed.

At this time, although not shown, a device with a roller or a tappet with a roller is incorporated at the end of the valve rod 7b of each mushroom valve 70, and a cylindrical cam or the like is used instead of the end cam-shaped cam disk 71. Alternatively, the rotary main shaft 20 may be formed as a central shaft 25 having no shaft column on the cam disk 71 side and a shaft column on only one side, and a pattern-shaped cam circle may be formed at the center of the back surface of the cam disk 71. A structure in which the plate shaft is fixed may be used. Also, the cam disk 7
One ridge-like projection has only one circumference, and the air chamber A,
The two mushroom valves 70, 70 for B may be joined and operated, and the oblique plate passage holes 4 communicating with the air chambers A, B may be used.
Each of 9 and 49 is formed in a plurality of holes, and the same number of mushroom valves 70 and 70 are attached to them.

[0216]

Embodiment 2 of Embodiment 15 In this respect, the embodiment based on Embodiment 4 in Embodiment 15 has two hemispheres incorporating four mushroom valves 70, 70, 70, 70 as shown in FIG. Fig. 7
In addition to the composition of the hemisphere shown in FIG. That is, the cam disk 71 shown in the embodiment of FIG.
The cam plate bearing 74 is provided with a cam plate bearing 74 having a circular hole penetrating the center thereof. Row board 4
The oblique plate connecting shaft 47 connecting the 0 and 40 is fitted and supported by the bearing.

The cam disk 71 is provided with a plurality of window-shaped holes radially provided in an outer portion closer to the outer peripheral surface than the ridge-shaped projections and having an arbitrary shape through its own thickness. The cam plate gear 76 of the bevel gear is disposed on the same circumference with a vertical line radiating from the center of the cam disk 71 as a mounting axis, and each of them is provided with teeth from both plate surfaces of the cam disk 71. Installed exposed. On the other hand, one of the parallel skew plates 40 is formed by engraving the edge circumference of the outer sliding contact surface 45 on a bevel gear skew plate ring gear 48 and the other skew plate. On the inner wall of the housing 10 on the side of 40, a housing fixed ring gear 18 of a bevel gear having the same pitch circle diameter as the skew plate ring gear 48 is provided as a fixed immovable gear. And housing fixed ring gear 18
Are aligned on the same line so that the tooth surfaces of each other face each other.

The cam disk 71 formed as described above is sandwiched between the swash plates 40, 40 arranged side by side, and the cam plate 71 is interposed between the swash plate ring gear 48 and the housing fixed ring gear 18. When a plurality of gears 76 are interposed and meshed with both, a plurality of cam plate gears 76
The cam disk 71 is rotated on the circumference of the housing fixed ring gear 18 at half the speed of the swash plate ring gear 48 while rotating itself with the rotation of 0, 40, and the cam disk 71 is rotated by the swash plate 40, 40 rotations. Rotate in the same direction at 1/2 the speed. Ultimately, the embodiment shown in FIG. 73 is such that a ridge-like projection is formed on the plate surface of a cam disk 71 which rotates at a half speed of the skew plates 40, 40 to form an original vehicle. The valve 70 is driven and operated in the same manner as in the case of the hemispherical composition in the embodiment of FIG. 72 to advance each stroke.

In the embodiment shown in FIG. 73, although not shown, the two skewing plates 40, 40, which are coaxially fixed, are separated from each other, and the two rotating main shafts 20, 20 are formed into an integral structure consisting of one long shaft. The housing 10 may be configured as a double wall penetrating in the long axis direction, and two cam disks 71 provided with the cam plate through holes 72 as shown in FIG. 72 may be mounted. Although not shown, the entire shape and composition are formed into four air chambers A, B, C, and D in a spherical shape, and the housing 10 at an appropriate position is formed.
Inlet holes In, which are provided through the wall, and over exhaust holes E
When the mushroom valves 70, 70, 70, 70 are arranged on x and Ex, a plane cam other than the cam disk 71 composed of an end cam or a three-dimensional cam may be arranged, or each mushroom valve 7.
Instead of 0, a piston-shaped piston valve 78 as shown in FIG. 74 may be arranged. In addition, the shape and device of the valve Va for opening and closing the flow passage holes In and Ex are arbitrary.

[0220]

Embodiment 16 Each of the above embodiments corresponds to a four-stroke cycle engine of a reciprocating piston engine. However, in the spherical rotary piston engine of the present invention, a two-stroke cycle engine is constructed and operated as described above. Is possible. Example 16 shown in FIG. 75 is similar to the example of the configuration based on Embodiment 1 described above, in which a circular rotary piston 30 and a skew plate 40 are incorporated in a spherical housing 10 to rotate the main spindle. 20 penetrates through the interior of the rotary piston 30 and the wall of the housing 10 to form four air chambers A, B, C, and D. There is a difference in the mounting of the valve device Va. In other words, the air chambers A and B in one half-moon working chamber Ha are the power (output) side Po for performing the expansion stroke due to the combustion of the compressed air and discharging the combustion gas, and the air chambers A and B in the other half-moon working chamber Ha. The chambers C and D are the pump (input) side Pu for performing the intake stroke and the compression stroke. Between the two half-moon working chambers Ha and Ha, a two-stroke cycle reciprocating piston engine (not shown) is provided. The housing communication hole 58 through which the working medium flows is equivalent to the scavenging hole of the housing 10.
Perforated in the wall.

The housing communication holes 58 are provided in the air chambers C and D.
Pump piston Pu at an appropriate position on the wall of the housing 10 facing the air chamber space in which the rotary piston 30 on the side faces the most contracted space corresponding to the top dead center.
The opening is opened, and the opening on the power (working) side Po is also opened on the air chambers A and B, facing the most contracted air chamber space where the rotating piston 30 at the top dead center can operate in the expansion stroke. At the same time, a mushroom valve 70 is inserted into the housing communication hole 58 in order to adjust the flow timing of the working fluid from the pump side Pu to the power side Po. In the embodiment of FIG. 75, two mushroom valves 70, 70 are connected. In addition, a cam driven by the rotating main shaft 20 or the localization rotating portion of the skewing plate 40 is driven as a prime mover.

[0222] The housing flow passage holes 15 and 15 in this embodiment have a circular shape of the rotary piston 30 corresponding to a position where one of the air chamber spaces is maximized and the other side is minimized in each half-moon shaped working chamber Ha. In the wall of the housing 10 (located on the negative side of the rotary piston 30 in FIG. 75) on the substantially extended plane of the plate, an intake port In shared by the air chambers C and D faces the half-moon working chamber Ha on the pump side Pu. , The exhaust chamber Ex shared by the air chambers A and B is the semi-lunar working chamber Ha on the power side Po.
Drilled facing. The suction and exhaust holes In, Ex
Is basically not fitted with a valve device such as a mushroom valve 70, and is also inserted into the igniter Ig basically in a manner facing the half-moon-shaped working chamber Ha on the power side Po. Is a wall of the housing 10 at a position where the air chamber space is contracted to a minimum with rotation, or is inserted into the housing communication hole 58 (not shown) located on the power side Po.

As described above, in FIG. 75, the pump-side Pu air chamber C has finished pushing out the compressed air toward the power-side Po air chamber A, and the mushroom valves 70,
Since the moment 70 is closed, the moved compressed air is already ignited. The air chamber C makes one revolution, which is equivalent to two strokes, from the start of intake to the end of compressed air feeding into the air chamber A,
One more rotation is required to complete the transfer of the compressed air to the air chamber A again, and one rotation is also required in the air chamber A from the start of the previous expansion stroke to the start of the expansion stroke in FIG. At the same time, the air chamber B on the power side Po and the pump side P
The same applies to the operation of the combination of u with the air chamber D.

That is, the air chamber A and the air chamber C, and the air chamber B and the air chamber D on the power side Po and the pump side Pu are all operated.
The power-side Po air chambers A and B perform an expansion stroke in each half rotation, and perform an exhaust stroke in the subsequent half rotation. When the air chamber A is in the expansion stroke, the air chamber B performs an exhaust stroke. ,
When the air chamber B is in the expansion stroke, the air chamber A performs the exhaust stroke, and also in the pump side Pu, when the air chamber C is performing the intake stroke with half a rotation, the air chamber D performs the compression stroke, and in the latter half of the compression stroke. Performs the transfer of the compressed air to the power-side Po air chamber B, and if the air chamber C starts compressing the intake air supply after a half rotation thereafter, the air chamber D pushes out the compressed air to start the next intake stroke.
Accordingly, the intake stroke of the air chamber C and the expansion stroke of the air chamber A,
The compression stroke and the exhaust stroke of the air chamber A are simultaneously proceeding, and the intake stroke of the air chamber D and the expansion stroke of the air chamber B, and the compression stroke of the air chamber D and the exhaust stroke of the air chamber B also proceed simultaneously. The two sets of the air chambers A, C and the air chambers B, D on the power side Po and the pump side Pu, which are given to each other, do not perform the same stroke simultaneously at the same time. C and D complete one cycle of two strokes in one rotation.

[0225]

Another embodiment of the sixteenth embodiment In the sixteenth embodiment, mushroom valves 70, 70 are inserted into the rotary piston 30 at both ends inside the piston intermediate shaft 33 as shown in FIG. Piston communication hole 3
Holes 6, 36 are drilled to operate a two-stroke cycle similar to the embodiment in FIG. That is, the two piston communication holes 36, 36 formed in the rotary piston 30 are
4 traverses both side portions in the piston intermediate shaft 33 which do not compete with each other, one of which communicates between the air chambers A and C and the other communicates between the air chambers B and D.

Each of the two mushroom valves 70, 70 with the valve heads 7a, 7a incorporated therein and the valve rods 7b, 7b directed toward the end of the piston intermediate shaft 33, is inserted into the two piston communication holes 36, 36. The piston intermediate shaft 33 is incorporated so as to be operable only in the column direction. In particular, valve stems 7b, 7b corresponding to tappet portions
Is inserted through the bottom surface of the piston intermediate shaft 33 and the swash plate ring 43, and although not shown, the inner surface circumference of the swash plate housing 10b is formed as a flat cam, and the circumference of the cam is The ends of the two valve stems 7b, 7b come into contact with each other with rotation and follow. As a result, when the air chambers A, B, C, and D rotate, either the air chamber C in the pump-side Pu half-moon working chamber Ha or one of the air chambers D at an appropriate point in the compression stroke, the piston communication hole of the air chamber. 3
6. Insert the end of the valve rod 7b inserted into the
b. The compressed air is moved to the pump side Pu air chamber C or the power side Po air chamber A provided with the air chamber D or the air chamber B by bringing the mushroom valve 70 up by rotating contact with the fixed cam on the inner surface of the b. .

When the mushroom valve 70 is opened, the air chamber C on the pump side Pu or the air chamber D on the power side Po at the end of the compression stroke of the air chamber D or the air chamber B on the power side Po has a void volume (clearance). (Volume) At the time corresponding to the top dead center, the end of the valve rod 7b comes out of contact with the fixed cam convex surface and is closed, and the power side Po air chamber A or the air chamber B performs an expansion stroke to give it. The pump-side Pu air chamber C or the air chamber D starts the intake stroke. At that time, the other air chamber C or the air chamber D on the pump side Pu starts the compression stroke, and the power Po air chamber A or the air chamber B applied thereto starts the exhaust stroke. , The mushroom valve 70 of the piston communication hole 36 is still closed.

[0228]

Embodiment 17 As a two-stroke cycle engine, Embodiment 17 shown in FIG. 77, in which two sets of element compositions equivalent to each other in a hemisphere based on the structure of the fourth embodiment, are united. The swash plate housings 10b, 10b are disposed on both sides of the rotating piston housings 10a, 10a, and a central portion in the housing 10 is formed in a housing partition 16 with the concave inner walls 11, 11 facing each other. However, the composition and arrangement of the two sets installed in the housing 10 thus configured are the same as the configuration of the ninth embodiment shown in FIG.

That is, the main bearings 13, 1 are mounted on the walls of the two oblique plate housings 10b, 10b on a straight line passing through the two ball centers O, O.
A central bearing 17 extends through the housing 3 and the housing partition 16. The rotating pistons 30, 30, each having a semi-circular plate shape, face each other with the spherical arc surfaces 32, 32 sandwiching the housing partition wall 16, and the swash plates 40, 40 are provided with swash plate through holes 44 on both sides thereof. , 44 are joined to the piston through holes 34, 34, respectively, and the piston through hole and the oblique plate through hole 3, which are provided to each other, are provided.
The rotating main shaft 20, into which the central bearing 17 and the two main bearings 13, 13 are inserted by loosely inserting the bearings 4, 44, 34, 44, is located at the two ball centers O, O and pivots on the rotating pistons 30, 30. To wear.

As shown in FIG. 77, between the pump side Pu and the power side Po, a housing communication hole 58 is formed so as to penetrate the housing partition 16 and the housing partition 16 looking into the hole has mushrooms. The valve 70 has the valve head 7a side in the housing 1
0 In the direction of the outer wall, the valve rod 7 b is inserted near the center of the housing 10 and is driven by a plate cam 77 of a flat cam attached to the center of the rotary spindle 20. In FIG. 77, if the semi-lunar working chamber Ha of the air chambers A and B is the power side Po performing the expansion stroke, and the semi-lunar working chamber Ha side of the air chambers C and D is the pump side Pu performing the intake stroke, The position of the intake port In and the exhaust port Ex, the power side P of the housing communication hole 58
The positions of the o port and the port Pu port on the pump side, and the operation of each stroke of the two-stroke cycle are the same as in the case of the sixteenth embodiment described above.

In FIG. 77, the swash plates 40, 40
Are arranged in an inverted C-shape, but parallel skew plates 40, 40 as shown in FIG. 61, and middle skew plates 40, 40 in the housing 10 as shown in FIG. Alternatively, as shown in FIG. 62, two sets of the rotating piston 30 and the skew plate 40 provided to each other may be arranged in parallel, and further, the outer sliding contact surfaces of the skew plates 40, 40 as shown in FIG. 4
The configuration may be such that the swash plate shafts 46, 46 protruding from the central portions of the swash plates 40 and the rotary piston 30 can be in any phase. Further, the igniter Ig is connected to the power Po as in the case of the sixteenth embodiment.
The housing 10 which looks inside the void volume chambers of the air chambers A and B or the inside of the housing communication hole 58 as shown in FIG.
The mushroom valve 7 is inserted into the wall and can be mounted on a flat cam.
If the mounting direction of 0 is changed, the swash plate ring 43 may be used.

[0232]

Embodiment 18 Further, as a two-cycle engine, Embodiment 18 shown in FIGS.
Is a configuration in which two sets of hemispherical compositions similar to each other in the same manner as in the seventeenth embodiment described above are united. However, the phase of the two skew plates 40 and The rotation main shafts 20 and 20 have a difference from the attachment of the communication holes communicating the semi-lunar working chambers Ha and Ha. It does not have independent movable parts such as 70.

That is, this embodiment is similar to the sixth embodiment shown in FIG.
b, 10b are coaxial with the axis of the internal surface formation and are integrated in the middle of the housing 10, and the rotating piston housings 10a, 10a on both sides thereof have concave inner walls 11, 1 of each other.
In the center of the housing 10 is a vertical housing partition 16 having a central bearing 17 at the center.
It is. Within the housing 10 so formed,
Each of the rotating pistons 30, 30 has a spherical surface 32, 3 of each other.
2 is arranged facing outward in the longitudinal direction of the housing 10,
The oblique plates 40, 40 are arranged side by side with the outer sliding contact surfaces 45, 45 facing each other with the housing partition wall 16 interposed therebetween. A swash plate connecting shaft 47 to be mounted is fixedly mounted to coaxially connect the two swash plates 40, 40, and each of the rotary main shafts 20 is formed by a shaft center 25 and a shaft column on one side only. , 20 are arranged in a C-shape in FIG. 78 when the main bearings 13, 13 provided thereto are fitted and inserted.

The communication holes connecting the power-side Po air chambers A and B and the pump-side Pu air chambers C and D are separately formed in each of the inclined plates 40 from the respective arcuate surfaces 41, 41 to the outer sliding contact surface 45. And two swash plate communication holes 68, 68 communicating with the housing, and a housing communication hole 58, which is a hole passing through the housing partition 16. The two swash plate communication holes 68, 6 of the same swash plate 40
8 open on the same rotating circle at a 180 ° center angle with respect to each other, and the housing communication hole 58 is provided with the air chambers A, B when the rotating pistons 30, 30 are located at the top dead center. , C,
It is perforated in the housing partition 16 (the lower part in FIG. 79) looking at D. After all, at the rotation angle position where each of the air chambers A, B, C, and D always shrinks the air chamber space, the left and right skewing plate communication holes 68, 68 with the housing communication hole 58 inside are three members. The compressed air in the pump-side Pu air chamber C or the air chamber D is moved to the power-side Po air chamber A or the air chamber B provided by the air chambers C and D by appropriately overlapping and joining on the same line.

In FIG. 78, the moment when the power-side Po air chamber A and the pump-side Pu air chamber C end the communication and the communication hole is closed, the air chamber A is closed. Is ignited and burns, and the air chamber C, which is also shrinking the air chamber space, is just before the end of the delivery of the compressed air and starts joining with the intake port In, and the air chamber B finishes the expansion stroke. Then, the exhaust stroke is started, and the air chamber D for expanding the air chamber space is disengaged from the connection with the intake port In and is at the position where the compression stroke is started. In the eighteenth embodiment, the swash plate communication hole 6 on the pump side Pu is used.
In order to prevent the compressed air from remaining in the swash plate 8, 68, for example, pin-shaped pistons 38, 38 as shown in FIG. When the air chambers C, D are expanded, the pin-shaped pistons 38, 38 are pulled out from the swash plate communication holes 68, and the pin-shaped pistons 38, 38 are inclined so that the air chamber space starts to contract. It is inserted into the row plate communication hole 68 to reduce the void volume in the hole.

[0236]

Another embodiment of the eighteenth embodiment As another embodiment of the eighteenth embodiment, even if the structure is as shown in FIGS. 80 and 81, it can be operated as a two-stroke cycle engine similar to the embodiment of FIGS. It is possible. The main difference in the configuration lies in the composition of the two swash plates 40, 40, which are provided to each other in the connection between the swash plates 40, 40 and the rotary pistons 30, 30 and communicate with each other for the movement of compressed air. This is the difference in hole mounting.

That is, as shown in FIG.
Nos. 0 and 40 are combined with each other on the outer sliding contact surfaces 45 and 45 without having the sloping plate ring 43, and each of them is projected on an axis line into which the piston intermediate shafts 33 and 33 are inserted. The hinge arms 53, 53, 53, 53 of the two mounting pins 51, 51, 51, 51 are provided. Also, the hinge arm 5 is attached to both piston intermediate shafts 33.
On both sides, two window-like cutout portions into which the holes 3 and 53 can be inserted are provided. Further, the holes of the hinge pin receivers 52 and 52 are provided in the direction of both ends continuously from the window-like cutouts. When the hinge joints 50 are formed by inserting the hinge pins 51, 51 attached to the hinge arms 53, 53 into the hinge pin receivers 52, 52, the oblique plates 40, 40 and the semi-circular rotary piston 30 are joined together at the back. , 30 are hingedly operatively connected.

In addition, the swash plate 40 is formed with a swash plate communication groove 69, which is formed by cutting the outer peripheral surface of the skewing plate 40 into a groove shape and bridges both plate surfaces.
Also, the inner wall corresponding to the joint where the two sets of housings 10 are joined has a housing communication groove 59 of a concave cutout portion. The two skewed plate communication grooves 69, 69, 69, 69 and the housing communication groove 59 thus formed are provided with the skewed plate communication holes 68, 68, 68, 68 having the configuration shown in FIGS. And the housing communication hole 58 are provided in the same positional relationship, and operate in a similar connection relationship. Also, the operation and progress of the two-stroke cycle performed by the air chambers A and B and the air chambers C and D are the same as in the embodiment shown in FIG. 78, and the igniter Ig is also the power side Po where the gap between the air chambers A and B is most contracted. Is inserted into the wall of the housing 10 facing the semi-lunar working chamber Ha, or the wall of the housing 10 at an appropriate position looking into the swash plate communication grooves 69 on the power side Po.

[0239]

Embodiment 19 Next, Embodiment 19 of the two-stroke cycle operation based on the structure of the first embodiment will be described with reference to FIGS. In the nineteenth embodiment, similarly to the configuration of the sixteenth embodiment, the whole shape of the housing 10 is formed into a spherical shape, and the rotary piston 30 of a circular plate and the skew plate 40 to be connected to the housing 10 are incorporated. Further, the valve device Va has a mushroom valve 7 similar to the configuration in the eighteenth embodiment.
0, etc., which have no independent movable parts and are opened and closed by intermittently connecting the stationary and movable communication holes, and the suction and exhaust holes In and Ex are attached in the same manner as in the above-described embodiment 16, and the ignition device Ig is also connected to the power side. It is inserted into the housing 10 wall of Po.

In the nineteenth embodiment, as shown in FIGS. 82 and 83, a fixed ball 80 of a spherical shape having a diameter smaller than the diameter of the piston intermediate shaft 33 and larger than the diameter of the rotary main shaft 20 is fixed in the center of the piston intermediate shaft 33. Incorporated in close relationship as part. The fixed ball 80 is provided with the housing communication hole 58 and the housing communication groove 59 on the immovable side in the above embodiment.
A fixed ball communication hole 82 of a through hole corresponding to the above is formed. Similarly, the communication hole on the movable side has a piston communication hole 36 that penetrates the piston intermediate shaft 33 and opens to each of the air chambers A, B, C, and D.
36, 36, 36 are opened on the circumference of the opening of the fixed ball communication hole 82, and each of the holes is applied to each of the opposed holes of the fixed ball communication hole 82 with the rotation of the piston intermediate shaft 33. The air chambers A and C or the air chambers B and D, which are inscribed and provided to each other, of the two half-moon working chambers Ha, Ha are separately communicated.

Note that a support rod 8 of a round column supporting the fixed ball 80
Reference numeral 1 denotes an end portion fixed to the fixed ball 80 and the rotating spindle 20
The inside of the rotary piston housing 10a
Since it is fixed to the wall, the inside of one of the rotating spindles 20 along its own axis is hollowed out into a tube, and a spindle rod 81 is inserted into the tube, and the end of the tubular shaft is Main bearing 1 mounted inside rotating piston housing 10a wall
Insert into 3. The central axis 25 formed of a circular plate of the rotating main shaft 20 is formed in an annular shape having a spherical inner peripheral surface with a central portion hollowed out concentrically. When the rotary shaft 20 is fitted so that it can be slidably contacted, one of the shaft columns of the rotary main shaft 20 is inserted into the support rod 81 attached to the fixed ball 80 and is fixed inside the wall of the housing 10, and the other shaft column is connected to the housing 10. It is supported by a main bearing 13 which has a shaft length that can be passed through and extends through the wall of the rotating piston housing 10a.

In this case, the piston pivot 35 formed in the space at the center of the inside of the rotary piston 30 faces each other while the horizontal wall at the center of the interior is cut out in a concave spherical crown shape. Since the inner spherical surface is formed by the spherical concave surface of the two spheres and the spherical inner surface of the central axis 25, the fixed sphere 80 is fitted into the inner spherical surface so as to be slidable. The fixed ball communication hole 82 penetrating the fixed ball 80
Is opened only at a position where one of the opposing holes can be connected to the half-moon-shaped working chamber Ha on the power side Po and the other hole can be connected to the half-moon-shaped working chamber Ha on the pump side Pu. And two pump communication ports 36, 3 in each of the half-moon working chambers Ha, Ha.
6, 36, 36, and opens on the rotation circumference of the hole.

Further, in this embodiment, although not shown, the main shaft gear 28 is attached to the end of the shaft of the rotary main shaft 20 on which the shaft rod 81 is inserted, and the main shaft gear 28 is externally meshed with the main shaft gear 28. If the joint shaft gear 23 is also mounted at an appropriate position on the wall of the housing 10, the output joint shaft 22 attached to the joint shaft gear 23 is projected and mounted as an output shaft in the same manner as in the configuration of Embodiment 14 shown in FIG. 69. Alternatively, the support rods 81 are provided not only on one side but also on opposite sides of the fixed sphere 80, and both side columns of the rotary main shaft 20 through which the support rods 81, 81 are inserted are formed in a tubular shape. Are rotatably fixed in the wall of the housing 10, and the above-mentioned main shaft gears 28, 28 are fixed to both ends of the shaft columns, and a joint shaft gear 23 provided to each of the main shaft gears 28, 28 is provided. ,
The output joint shafts 22, 22 having 23 may be mounted at appropriate positions on the opposing wall of the housing 10.

[0244]

According to the spherical rotating piston engine of the present invention having the above-described structure and operation, a high piston speed can be obtained by eliminating the crankshaft from the engine shaft to eliminate the reciprocation of the piston and by adopting the spherical structure. At the same time, it exhibits various excellent performances. In other words, resolving the inertial force of the reciprocating mass due to the reciprocating acceleration movement of the piston pushes the upper limit of the average piston speed to widen the operating rotation range of the engine, and means high speed rotation of the engine, thereby achieving high output, The higher the rotation speed, the higher the specific output of PS / l, so that the fuel efficiency is necessarily improved.

Also, exhaust gas, quietness, durability, weight, production cost, combustion state, cooling, oil film lubrication, wear resistance,
In order to satisfy various indispensable conditions for an internal combustion engine, such as airtightness maintenance and mechanical mechanics, the engine has a spherical and spherical basic structure. That is, the ratio of the stroke volume to the engine volume is remarkably large by making the basic structure a spherical shape having the maximum volume and the minimum surface area in the three-dimensional shape,
The engine is extremely lightweight and compact because it has no crank mechanism, has a double-ended piston, and has four air chambers corresponding to four cylinders in a reference sphere. Furthermore, since the rotating body capable of rotating inside the sphere according to the present invention can be formed symmetrically with respect to the axis of rotation, the moment of inertia is small, the transient characteristics are excellent, and the mechanical efficiency is high due to the rotational movement, and the vibration is excellent.・ Small noise is generated, and the sphere, which is the engine body, is robust against thermal deformation, stress and impact load.

Each of the main components including the rotary piston 30, the skew plate 40, the rotary spindle 20, and the valve device Va is simple, the number of components is small, the number of the same components is small, and the mechanism is simple and plain. Not complicated. In other words, there is no assembling of the same parts and the same device, and the simplicity of the mechanism is advantageous for workability such as disassembly, assembling, and maintenance. Needless to say, it is low in cost, hard to break down, and durable.

The working chamber formed in the sphere is approximately 1: 1.
In contrast to the reciprocating piston engine having the ratio of bore diameter and stroke (the most demanding automobile engine), the flat comb-shaped working chamber Fu of the present invention has a remarkably large ratio of area to volume and spherical surface. Due to the fact that the working chamber is constantly moving in the concave surface of the above, the inflow air is disturbed and agitated. As a result, flame propagation in the combustion chamber progresses and complete combustion is promoted,
High combustion efficiency is obtained by suppressing the generation of harmful CO and the emission of unburned HC gas due to incomplete combustion, but the flame is cooled by the combustion chamber wall due to the large surface area of the combustion chamber wall where the flame contacts. The maximum combustion temperature is low, and the generation of NOx of harmful exhaust gas generated at high temperatures and the occurrence of abnormal combustion are small.

The fact that the combustion temperature is low means that the engine can be manufactured using inexpensive materials of lower quality from the viewpoint of heat resistance, but the combustion chamber which moves with the combustion in the sphere, especially the combustion. Is that the combustion heat is transmitted and diffused to the combustion chamber wall to make the temperature of the entire engine uniform,
Suppresses strength reduction and bimetallic thermal deformation. In addition to the low combustion temperature, the engine body, in which a plurality of combustion chambers are gathered on the same sphere, does not require a large-sized, large-capacity cooling device for high temperature and high cooling performance, and also has a piston through-hole. By forming the combination of 34 and the rotating main shaft 20 in an oil pump, the generation and cooling of the lubricating oil film at the engine pivot can be performed simultaneously.

In the rotating body of the present invention having a notch formed with a sphere, it is sufficient that a circular airtight device corresponding to a piston ring is fitted on the rotating circumferential surface, and the rotating outer circumferential surface of the rotating body is in the housing 10 of the working chamber. Since it is in surface contact with the wall surface, it is advantageous in terms of both the formation of a lubricating oil film and the maintenance of airtightness, and the same airtightness is shared by a plurality of working chambers, so that the same subdivided parts do not come out, and a rotating body consisting of a circular body The rotational load of the body is distributed over the circular contact surface, which is advantageous for wear resistance. In other words, in a reciprocating piston engine, for example, the piston ring cuts the cylinder inside which should be a perfect circle by the reciprocating acceleration movement of the piston in the crank rotation direction and deforms it into an elliptical shape. However, the spherical rotating piston engine of the present invention does not have a deformation element of the working chamber due to the reciprocating frictional resistance and no elements that generate a lead cross due to frictional wear.

On the other hand, the intake and exhaust valves are not concentrated at one location only at the cylinder head as in a reciprocating piston engine, have a degree of freedom in the diameter range of the intake and exhaust holes, and have a mutual volume. Are inversely proportional to each other, and the two comb-shaped working chambers Fu, Fu forming a pair continuously perform the intake stroke and the exhaust stroke. Excellent, can take in more intake air weight and obtain high average effective pressure value.

Alternatively, when the spherical rotary piston engine of the present invention is configured as a two-stroke cycle engine, basically, since a suction and exhaust valve mechanism is not required, a blockage of the flow of inflow / outflow air as a working medium is obstructed. Since there is no portion or a constricted portion where the flow velocity resistance increases, pumping loss due to flow path resistance, back pressure, etc. is reduced. Further, the working chamber on the pump side Pu continuously sucks the working medium without stopping, and the power side Po.
Even in this case, there is no periodic on / off because the combustion gas is continuously discharged unilaterally, continuity is generated in each stroke, the inertial weight of the air works effectively, and the joint between the strokes on the suction and discharge sides. Pump loss, mechanical loss is small,
High suction and exhaust efficiencies can be obtained, and the continuous combustion and expansion strokes also reduce heat loss, resulting in high combustion efficiency.

In addition, since the high temperature side of the combustion and the low temperature side of the fresh air intake are completely separated from each other and there is no mechanism operation in which the piston moves in both directions, the engine is not affected by the thermal stress. At the same time, the air density does not decrease after the combustion stroke, and the charging efficiency of the intake air does not decrease, and the intake fresh air does not expand to reduce the intake air volume. Further, when the working medium moves from the pump-side Pu air chamber to the power-side Po air chamber, the flow velocity increases, and turbulence and eddy currents are likely to occur in the flow. Because it improves the flame speed of combustion and enables turbulent flame propagation,
High thermal efficiency can be obtained to improve combustion efficiency and complete combustion. Then, the pump side Pu air chamber and the power side Po
If the stroke volume ratio to the air chamber is set to a value other than 1: 1, the generated torque can be adjusted by increasing or decreasing the amount of intake air.

As described above, the present invention has a structure and operation based on a completely different principle from the conventional reciprocating piston engine, and the conventional reciprocating piston engine is inconsistent and cannot be solved. This is a high-performance rotary piston engine that achieves both high output and excellent fuel economy by realizing both power and fuel economy. In addition, the realization of the high-performance engine according to the present invention has low harmfulness of exhaust gas, has no harmfulness, there is no difficulty in parts and composition, there is no difficulty, the number of parts is small, and handling is easy. Due to its simplicity, the manufacturing cost is greatly reduced and inexpensive. In addition, it is a durable product, lightweight and compact, and has a number of excellent effects, such as a quiet engine that suppresses the generation of vibration and noise.

[Brief description of the drawings]

FIG. 1 is a partially longitudinal perspective view of a basic graphic showing the principle of the present invention.

FIG. 2 is a perspective view showing an angle change of a reference graphic.

FIG. 3 is a perspective view showing an angle change of a reference graphic.

FIG. 4 is a perspective view showing a change in angle of a reference graphic.

FIG. 5 is a perspective view showing a change in the angle of a reference graphic.

FIG. 6 is a perspective view showing a change in the angle of a reference graphic.

FIG. 7 is a perspective view showing a change in angle of a reference graphic.

FIG. 8 is a perspective view showing a change in the angle of a reference graphic.

FIG. 9 is a partially longitudinal side view showing the first embodiment of the present invention.

FIG. 10 is an exploded perspective view, partly in section, of FIG. 9;

FIG. 11 is a partially longitudinal side view showing the second embodiment of the present invention.

FIG. 12 is an exploded perspective view, partly in section, of FIG. 11;

FIG. 13 is a partially longitudinal side view showing the third embodiment of the present invention.

FIG. 14 is an exploded perspective view, partly in section, of FIG. 13;

FIG. 15 is a partially longitudinal side view showing the fourth embodiment of the present invention.

FIG. 16 is an exploded perspective view, partly in section, of FIG. 15;

FIG. 17 is a partially exploded perspective view showing a pin joint joint according to the present invention.

FIG. 18 is a partially sectional exploded perspective view showing a pin joint joint according to the present invention.

FIG. 19 is a partially sectional exploded perspective view showing a pin joint joint according to the present invention.

FIG. 20 is a perspective view of (i), (ro), (ha), and (ii) showing the operation of the rotating main shaft and the rotating piston in the present invention.

FIG. 21 is a perspective view of (H), (F), (F), and (C) showing the operation of the rotating main shaft and the rotating piston, continued from FIG. 20;

FIG. 22 is a partial vertical sectional side view of (A), (B), (C), (D), (E), and (F) showing a volume change of each air chamber in the present invention.

FIG. 23 is a partial longitudinal sectional side view of (G), (H), (I), (J), (K), and (L) showing a volume change of each air chamber, continued from FIG. 22;

FIG. 24 shows the operation of four strokes in the present invention (A).
(A) (c) (d) (e) (f) Partial longitudinal side view.

FIG. 25 shows the operation of the four strokes continued from FIG. 24 (g)
(C) (K) (K) (S) (S) each partially longitudinal side view.

FIG. 26 is a partially longitudinal front view showing the principle of torque generation in the present invention.

FIG. 27 is a partially longitudinal side view showing the first embodiment of the present invention.

FIG. 28 is a perspective view showing a ring valve (１ ／ rotation speed) and a valve train according to the first embodiment;

FIG. 29 is an exploded perspective view of FIG. 27 (Example 1).

FIG. 30 is a side view showing a swash plate flow path hole according to the first embodiment.

FIG. 31 is an exploded perspective view, partly in section, showing a swash plate passage hole, a valve connection hole, and a housing passage hole of the first embodiment;

FIG. 32 is a partial cross-sectional front view showing the connection of the outflow / inflow holes in FIG. 31.

FIG. 33 is a schematic diagram of a partially longitudinal front view of each of (a) to (a) and (a) to (d) showing the operation of four strokes in the first embodiment.

FIG. 34 is a partially longitudinal side view showing Embodiment 2 of the present invention.

FIG. 35 is a partially cutaway perspective view showing a ring valve (１ ／ rotation speed) of the second embodiment.

FIG. 36 is an exploded perspective view, partially in section, of FIG. 34 (Example 2);

FIG. 37 is a side view showing a swash plate passage hole according to the second embodiment.

FIG. 38 is an exploded perspective view, partly in section, showing a swash plate passage hole, a valve connection hole, and a housing passage hole according to the second embodiment.

FIG. 39 is a partial cross-sectional front view showing the connection of the outflow / inflow holes in FIG. 38;

FIG. 40 is a schematic view of a partly longitudinal front view of (a-d) and (a-d) showing the operation of four strokes in the second embodiment.

FIG. 41 is a partially cutaway perspective view showing a ring valve (3/4 rotational speed) of the second embodiment.

42 (a) to (d) and (a) to (b) are schematic views of the front view in a partially longitudinal direction, respectively, showing an operation in four strokes when the ring valve of FIG. 41 is mounted.

FIG. 43 is a partially cutaway perspective view showing a ring valve (5/6 rotation speed) of the second embodiment.

44 (a) to (d) and (a) to (b) are schematic views of the front view in a partially longitudinal direction, respectively, showing an operation in four strokes when the ring valve of FIG. 43 is mounted.

FIG. 45 is a partially cutaway perspective view showing the ring valve (7/8 rotation speed) of the second embodiment.

FIG. 46 is a schematic view in front of a part of each of (a-d) and (a-d) showing the operation of four strokes when the ring valve of FIG. 45 is mounted.

FIG. 47 is a partially longitudinal side view showing the third embodiment of the present invention.

FIG. 48 is a perspective view showing a ring valve (１ ／ rotation speed) of the third embodiment.

FIG. 49 is an exploded perspective view in partial section of FIG. 47;

FIG. 50 is a partially longitudinal side view showing Example 4 of the present invention.

FIG. 51 is a perspective view showing a plate valve (１ ／ rotation speed) according to a fourth embodiment;

FIG. 52 is a partially longitudinal side view showing Example 5 of the present invention.

FIG. 53 is a partially longitudinal side view showing Example 6 of the present invention.

FIG. 54 is a partially cutaway perspective view showing a plate valve (１ ／ rotation speed) of the sixth embodiment.

FIG. 55 is an exploded perspective view partially in section of FIG. 53;

FIG. 56 is a partially longitudinal sectional side view of each of (a), (b), and (c) showing a mounting range of both rotating spindles in the fourth embodiment.

FIG. 57 is a partially longitudinal side view showing the seventh embodiment of the present invention.

FIG. 58 is a partially longitudinal side view showing Example 8 of the present invention.

59 is perspective views of (a) and (b) showing two ring valves (1/2 rotation speed) in Embodiment 8. FIG.

FIG. 60 is an exploded perspective view partially in section of FIG. 58;

FIG. 61 is a partial longitudinal sectional side view of each of (a), (b) and (c) showing both skew plate attaching axes in the ninth embodiment and the fourth embodiment of the present invention.

FIG. 62 is a partial longitudinal side view showing the tenth embodiment of the present invention.

FIG. 63 is a partially longitudinal side view showing an eleventh embodiment of the present invention.

FIG. 64 is a partially cutaway side view showing a plate valve and a valve gear according to an eleventh embodiment.

FIG. 65 shows two sets of connection in the fourth embodiment (a).
(B) (c) (d) Partial longitudinal side view of each.

FIG. 66 is a partially longitudinal plan view showing a twelfth embodiment of the present invention.

FIG. 67 is a partially longitudinal side view showing Embodiment 13 of the present invention.

FIG. 68 is a perspective view showing a ring valve (１ ／ rotation speed) of the thirteenth embodiment;

FIG. 69 is a partially longitudinal side view showing a fourteenth embodiment of the present invention.

FIG. 70 is a side view showing the ring valve (１ ／ rotation speed) of the fourteenth embodiment;

FIG. 71 shows the operation of the four strokes in Example 14 (a
FIGS. 6A to 6B are schematic partial vertical sectional views, and perspective views of FIGS. 6A to 6D showing changes in the rotation angle of the ring valve.

FIG. 72 is a partial longitudinal side view showing Example 15 (Aspect 1) of the present invention.

FIG. 73 is a partially longitudinal side view showing Example 15 (Aspect 2) of the present invention.

FIG. 74 is a partial cross-sectional side view showing a piston valve according to Embodiment 15.

FIG. 75 is a partial longitudinal sectional side view showing a sixteenth embodiment of the present invention, and a partial sectional side view showing a housing communication hole and a valve device.

FIG. 76 shows another embodiment of the sixteenth embodiment (piston communication hole and valve).
FIG.

FIG. 77 is a partially longitudinal side view showing Example 17 of the present invention.

FIG. 78 is a partially longitudinal side view showing Example 18 of the present invention.

FIG. 79 is an exploded perspective view, partly cut away, showing a swash plate communication hole and a housing communication hole of Embodiment 18;

FIG. 80 is a partially longitudinal side view showing another embodiment of the eighteenth embodiment.

FIG. 81 is an exploded perspective view, partly cut away, showing a swash plate communication groove, a housing communication groove, and a hinge pin shown in FIG. 80;

FIG. 82 is a partially longitudinal side view showing a nineteenth embodiment of the present invention;

FIG. 83 is an exploded perspective view, partially in section, showing a fixed ball and a central axis according to a nineteenth embodiment;

[Explanation of symbols]

G sphere O sphere center of sphere G r radius of sphere G X X-axis (axis of rotation main axis) Y Y-axis (axis of formation of S-circle, rotation axis of oblique plate) θ θ angle (X-axis and Y-axis) P (Point where the X axis intersects the spherical surface G) Q Q Point (Point where the Y axis intersects the spherical surface G) U Conical locus U (Points P and Q are the diameter bottom surface, spherical center O M M axis (vertical axis of X axis, connecting axis of pin joint joint) R R circular surface (horizontal circular surface on X axis) S S circular surface (vertical circular surface of Y axis line) L L axis (rotation axis of R surface) K K axis (intersecting line of R surface and S surface, connection axis of hinge joint) Ka One end point of both ends of K axis Kb The other end point of both ends of K axis Half-moon-shaped space, half-moon-shaped working chamber Fu Comb-shaped space, comb-shaped working chamber In Intake hole Ex Exhaust hole Ig Igniter, or fuel Slamming valve Va Valve device, valve A space, working chamber, swash plate passage hole B communicating with air chamber A space, working chamber, swash plate passage hole C communicating with air chamber B space, working chamber, air Swash plate passage hole D communicating with chamber C Space, working chamber, swash plate passage hole communicating with air chamber Du Pump side, input side Po working, power side, output side 10 housing 10a rotating piston housing 10b Swash plate housing 11 Concave inner wall of rotating piston housing 12 Track gap 13 Main bearing 14 Skew plate bearing 15 Housing flow passage hole 5a Inner opening of housing flow passage hole 16 Housing partition 17 Central bearing of housing partition 17 Housing fixed ring gear 19 Valve raceway 20 Rotating main shaft 22 Output joint shaft 23 Joint shaft gear 25 Center shaft 27 Valve gear 28 Main shaft gear 30 Rotating piston 31 Rotating piston bow Form surface 32 Spherical surface of rotating piston 33 Piston intermediate shaft 34 Piston through hole 35 Piston pivot 36 Piston communication hole 38 Pin-shaped piston 39 Intermediate shaft cut 40 Slanting plate 40a Slanting plate body 40b Slanting plate retaining frame 41 Slanting Bow-shaped surface of row plate 42 Chord side surface of swash plate 43 Skew plate ring 44 Skew plate shaft hole 45 Sliding plate outer sliding contact surface 46 Skew plate shaft 47 Skew plate connection shaft 48 Skew plate ring gear 49 Oblique plate passage hole 9b Outer opening of swash plate passage hole 50 Hinge joint 51 Hinge pin 52 Hinge pin receiver 53 Hinge arm 54 Intermediate gear 55 Pin joint joint 58 Housing communication hole 59 Housing communication groove 60 Ring valve 61 Plate Valve 62 Valve ring gear 64 Valve plate bearing 65 Valve passage hole 66 Valve connection hole 6a Inward opening of valve connection hole 6b Outward opening of valve connection hole 68 Skew plate communication hole 6 Slant plate communication groove 70 Mushroom valve 7a Mushroom valve valve head 7b Mushroom valve valve stem 7c Mushroom valve valve spring 71 Cam disk 72 Cam plate through hole 73 Cam ring gear 74 Cam plate bearing 75 Cam plate drive gear 76 cam plate gear 77 plate cam 78 piston valve 80 fixed ball 81 fixed ball support rod 82 fixed ball communication hole

Claims (4)

[Claims] 1. A housing (10) formed on an inner wall surface which forms a spherical surface (G) having a radius (r) from a spherical center (O) and forms an angle (θ) and intersects at the spherical center (O). Let the two fixed axis straight lines be the axis (X) axis (Y), the point where the axis (X) intersects the spherical surface (G) be the point (P), and the point where the axis (Y) intersects the spherical surface (G) be the point (Q), the point (P), the path between the points (Q), the diameter of the bottom surface, the trajectory of the cone having the sphere (O) as the apex, the trajectory of the cone (U), and the axis (X) at the sphere (O) A large circular plane in a spherical surface (G) having an axis (M) as an axis line perpendicular to the axis (M), a horizontal plane on the axis (X), and an axis (L) of the diameter line as a rotation axis is a circular surface (R). A large circular plane formed through the spherical center (O) in the spherical surface (G) with the axis (Y) as a vertical axis is defined as a circular surface (S), and the circular surface (R) And the circle (S) intersect at the sphere center (O), the axis (K) is defined as the axis (K), and both ends of the intersection (K) are defined as points (Ka) and points (Kb). (1)
In (0), the inner wall of the housing (10) on the plane extending from the circular surface (S) is cut into the raceway gap (12) of the orbital groove, and the housing (10) through which the axis (X) passes is formed. ),
(13) is provided, and the main bearings (13) and (13) are provided with bearings for both shafts and necks of a rotating main shaft (20) having a linear shape, and are positioned at the spherical center (O) of the rotating main shaft (20). It has a central axis (25) consisting of either a pin post or a pin receiving hole of a pin joint joint (55) having an axis (M) as a connection axis, and a spherical surface (G) on a circular surface (R). Housing (10)
The arcuate surface of the opposing outer peripheral surface that rotatably contacts the inner wall surface (3
2), (32) and the arcuate surfaces (32), (32), and the arcuate surfaces (31), (31), (31), (31), (31) (31) and a substantially circular plate rotating piston (30) in which a cylindrical piston intermediate shaft (33) is interposed and combined on the chord side thereof, and this rotating piston (30) has two spherical arc surfaces (32). , (3
2) A piston passage hole (34) for allowing the rotary main shaft (20) to be loosely inserted is opened and the piston passage hole (34).
In the center, there is provided a piston pivot (35) of a connecting element corresponding to the central pivot (25), and a rotating main shaft (20) on the axis (X).
, The angle (± θ) range is pivotably connected to the piston and the point (Ka) point (K) at both ends of the piston intermediate shaft (33).
b) hinge pin (51) of the hinge joint (50) element on the side,
(51) or hinge pin receivers (52), (52) are provided, and the arcuate surfaces (41), (4)
1), (41), (41) and the chord side faces (4) which face each other in sliding contact with the column face of the piston intermediate shaft (33).
An annular swash plate ring (4) that rotatably fits into the raceway gap (12) on the two arcuate plates formed from (2) and (42).
3), a circular plate-shaped inclined plate (4)
0), and the swash plate (40) is provided on both sides of the swash plate ring (43) located on the point (Ka) point (Kb) side, with a connection corresponding to the hinge joint (50) element. The hinge joint (50) is fitted with the element and the swash plate (40) and the rotating piston (3) are fitted.
0) and the angle (± θ) with the dividing line (K) as the axis of the hinge
The swash plate (40) on the circular surface (S) closes the inner wall surface of the housing (10) forming a spherical surface (G), and the two sloping plates (40) on the circular surface (S) are each formed of a hemispherical space. Half moon working chamber (Ha), (Ha)
And each of the half-moon-shaped working chambers (Ha) and (Ha) is formed into four working chambers (Fu) and (Fu) in which two rotating pistons (30) on the circular surface (R) form two comb-shaped spaces. Fu), (F
u) and (Fu), and further open and close the working medium suction hole (In) and the working medium passage (Ex) and the passage of the working medium appropriately to the semi-lunar working chambers (Ha) and (Ha). A spherical rotary piston engine provided with a valve device (Va) and fitted with an igniter (Ig) or a fuel injection valve looking into a combustion chamber. 2. A housing (10) formed on an inner wall surface which forms a spherical surface (G) with a radius (r) from the spherical center (O) forms an angle (θ) and intersects at the spherical center (O). Let the two fixed axis straight lines be the axis (X) axis (Y), the point where the axis (X) intersects the spherical surface (G) be the point (P), and the point where the axis (Y) intersects the spherical surface (G) be the point (Q), the point (P), the path between the points (Q), the diameter of the bottom surface, the trajectory of the cone having the sphere (O) as the apex, the trajectory of the cone (U), and the axis (X) at the sphere (O) A large circular plane in a spherical surface (G) having an axis (M) as an axis line perpendicular to the axis (M), a horizontal plane on the axis (X), and an axis (L) of the diameter line as a rotation axis is a circular surface (R). A large circular plane formed through the spherical center (O) in the spherical surface (G) with the axis (Y) as a vertical axis is defined as a circular surface (S), and the circular surface (R) And the circle (S) intersect at the sphere center (O), the axis (K) is defined as the axis (K), and both ends of the intersection (K) are defined as points (Ka) and points (Kb). (1)
0) is divided into two sides by a parallel plane of the circular surface (S) and the spherical surface (G)
Of the working chamber and the axis (Y) of a hemispherical space having an inner wall surface
The main bearing (1) is formed on a wall of a housing (10) through which an axis (X) penetrates and is formed at a portion of a raceway gap (12) having an inner peripheral surface having an inner diameter longer than a radius (r) of a concentric circle.
3) is provided, and the main bearing (13) is supported by the shaft and neck of the rotating main shaft (20), which is in the form of a straight axis, and is connected to the axis (M) at the spherical center (O) of the rotating main shaft (20). Pin joint joint as shaft (55)
Shaft center (2) consisting of either a pin post or a pin receiving hole
5), a housing (10) having a spherical surface (G) on a circular surface (R)
The arcuate surface (32) of the outer peripheral surface rotatably in contact with the inner wall surface and the arcuate contour plane of the arcuate surface (32) and the front and back arcuate surfaces (31), (31) having the chord on the axis (K) side ) And a columnar piston intermediate shaft (33) on its chord side are provided with a substantially semi-circular rotating piston (30), and the rotating piston (30) has a rotating surface on a spherical arc surface (32). A piston through-hole (34) through which the main shaft (20) is loosely inserted is opened, and a coupling element corresponding to the shaft center pivot (25) is formed at the center of the piston through-hole (34) in the piston intermediate shaft (33). A piston pivot (35) is provided to pivotably pivot within a range of an angle (± θ) with respect to the rotating main shaft (20) on the axis (X), and the point (Ka) at both ends of the piston intermediate shaft (33). Hinge pin (51), (51) or hinge pin of hinge joint (50) element on point (Kb) side (52), (5
2), and the arcuate surfaces (41), (41) and both arcuate surfaces (41), (41), (2) are provided on both sides of the intermediate surface (33) of the piston on the axis (K) on the circular surface (S). 41), the piston intermediate shaft (3
3) An outer sliding contact surface (45) in which the chordal side surface (42) formed of a groove-shaped concave surface that is in sliding contact with the column surface and the back surfaces of both arcuate surfaces (41) and (41) are formed on the same rotation surface. An annular swash plate (40) is formed by combining an annular swash plate ring (43) rotatably fitted in the raceway gap (12) with the circular plate formed from the above and forming an outer peripheral surface. The skew plate (40) is provided with connecting elements corresponding to the hinge joint (50) elements on both sides of the skew plate ring (43) located on the point (Ka) point (Kb) side. The hinge joint (50) is fitted and the swash plate (40) and the rotating piston (3)
0) and the angle (± θ) with the dividing line (K) as the axis of the hinge
The swash plate (40) on the circular surface (S) closes the inner wall surface of the housing (10), which forms a spherical surface (G), so that the inner wall surface of the housing (10) forms a hemispherical space. (Ha) is formed, and the half-moon-shaped working chamber (Ha) is formed into two working chambers (Fu) and (Fu) in which the rotating piston (30) on the circular surface (R) forms a comb-shaped space; Further, a suction port (In) and a discharge port (Ex) of the working medium and a valve device (Va) for appropriately opening and closing the passage of the working medium are provided facing the half-moon-shaped working chamber (Ha), and ignition is performed by looking at the combustion chamber. A spherical rotating piston engine having a tool (Ig) or a fuel injection valve inserted therein. 3. A housing (10) formed on an inner wall surface which forms a spherical surface (G) with a radius (r) from the spherical center (O) forms an angle (θ) and intersects at the spherical center (O). Let the two fixed axis straight lines be the axis (X) axis (Y), the point where the axis (X) intersects the spherical surface (G) be the point (P), and the point where the axis (Y) intersects the spherical surface (G) be the point (Q), the point (P), the path between the points (Q), the diameter of the bottom surface, the trajectory of the cone having the sphere (O) as the apex, the trajectory of the cone (U), and the axis (X) at the sphere (O) A large circular plane in a spherical surface (G) having an axis (M) as an axis line perpendicular to the axis (M), a horizontal plane on the axis (X), and an axis (L) of the diameter line as a rotation axis is a circular surface (R). A large circular plane formed through the spherical center (O) in the spherical surface (G) with the axis (Y) as a vertical axis is defined as a circular surface (S), and the circular surface (R) And the circle (S) intersect at the sphere center (O), the axis (K) is defined as the axis (K), and both ends of the intersection (K) are defined as points (Ka) and points (Kb). (1)
In (0), the inner wall of the housing (10) on the plane extending from the circular surface (S) is cut into the raceway gap (12) of the orbital groove, and the housing (10) through which the axis (X) passes is formed. ),
(13) is provided, and the main bearings (13) and (13) are provided with bearings for both shafts and necks of a rotating main shaft (20) having a linear shape, and are positioned at the spherical center (O) of the rotating main shaft (20). It has a central axis (25) consisting of either a pin post or a pin receiving hole of a pin joint joint (55) having an axis (M) as a connection axis, and a spherical surface (G) on a circular surface (R). Housing (10)
The arcuate surface (32) of the outer peripheral surface that is larger than the hemispherical surface, which is rotatably in contact with the inner wall surface and straddles the circular surface (S), forms an arcuate contour plane of the arcuate surface (32). ) On both sides of the arcuate surface (31), (31) and both arcuate surfaces (3)
A rotating piston (30) of a hemispherical circular plate having a cylindrical piston intermediate shaft (33) interposed therebetween is disposed between 1) and (31), and the rotating piston (30) has a spherical arc surface (32). A piston through hole (34) through which the rotating main shaft (20) is loosely inserted is opened on both sides opposite to each other, and a connecting element corresponding to the shaft center pivot (25) is formed at the center of the piston through hole (34). A rotating shaft (2) on an axis (X) is provided with a piston pivot (35).
0), the hinge pin (5) of the hinge joint (50) element is pivotally connected to the point (Ka) point (Kb) on both ends of the piston intermediate shaft (33) at the angle (± θ) range swingably.
1), (51) or hinge pin receivers (52), (52) are provided, and the front and back bow-shaped surfaces (41), (41) are provided on the circular surface (S).
The orbital gap (1) is formed in an arcuate plate formed by the armature and the chordal side surface (42) which comes into sliding contact with the column surface of the piston intermediate shaft (33).
A circular plate-shaped swash plate (40) having an outer peripheral surface formed by combining an annular swash plate ring (43) rotatably fitted to 2) is disposed. A connecting element corresponding to the hinge joint (50) element is provided on both sides of the skewed plate ring (43) located on the point (Ka) point (Kb) side, and the hinge joint (50) is skewed. Plate (40) and rotating piston (3
0) and the angle (± θ) with the dividing line (K) as the axis of the hinge
The swash plate (40) on the circular surface (S) is formed into a hemispherical space with the inner wall surface of the housing (10) forming a spherical surface (G) separated on both sides. Working chambers (Ha), (H
a), and each of the semi-lunar working chambers (Ha) and (Ha) is formed in a working chamber (Fu) or (Fu) in which a rotating piston (30) on a circular surface (R) forms a comb-shaped space. Further, a valve device (Va) for opening and closing the suction hole (In) and the discharge hole (Ex) of the working medium and appropriately opening and closing the passage of the working medium is provided facing the half-moon working chambers (Ha) and (Ha); A spherical rotating piston engine having an ignition device (Ig) or a fuel injection valve inserted into a combustion chamber. 4. A housing (10) formed on an inner wall surface which forms a spherical surface (G) with a radius (r) from the spherical center (O) and forms an angle (θ) and intersects at the spherical center (O). Let the two fixed axis straight lines be the axis (X) axis (Y), the point where the axis (X) intersects the spherical surface (G) be the point (P), and the point where the axis (Y) intersects the spherical surface (G) be the point (Q), the point (P), the path between the points (Q), the diameter of the bottom surface, the trajectory of the cone having the sphere (O) as the apex, the trajectory of the cone (U), and the axis (X) at the sphere (O) A large circular plane in a spherical surface (G) having an axis (M) as an axis line perpendicular to the axis (M), a horizontal plane on the axis (X), and an axis (L) of the diameter line as a rotation axis is a circular surface (R). A large circular plane formed through the spherical center (O) in the spherical surface (G) with the axis (Y) as a vertical axis is defined as a circular surface (S), and the circular surface (R) And the circle (S) intersect at the sphere center (O), the axis (K) is defined as the axis (K), and both ends of the intersection (K) are defined as points (Ka) and points (Kb). (1)
0) is divided into two sides by a parallel plane of the circular surface (S) and the spherical surface (G)
Of the working chamber and the axis (Y) of a hemispherical space having an inner wall surface
The main bearing (1) is formed on a wall of a housing (10) through which an axis (X) penetrates and is formed at a portion of a raceway gap (12) having an inner peripheral surface having an inner diameter longer than a radius (r) of a concentric circle.
3) is provided, and the main bearing (13) is supported by the shaft and neck of the rotating main shaft (20), which is in the form of a straight axis, and is connected to the axis (M) at the spherical center (O) of the rotating main shaft (20). Pin joint joint as shaft (55)
Shaft center (2) consisting of either a pin post or a pin receiving hole
5), a housing (10) having a spherical surface (G) on a circular surface (R)
The arcuate surface (32) of the outer peripheral surface rotatably in contact with the inner wall surface and the arcuate contour plane of the arcuate surface (32) and the front and back arcuate surfaces (31), (31) having the chord on the axis (K) side ) And a columnar piston intermediate shaft (33) on its chord side are provided with a substantially semi-circular rotating piston (30), and the rotating piston (30) has a rotating surface on a spherical arc surface (32). A piston through-hole (34) through which the main shaft (20) is loosely inserted is opened, and a coupling element corresponding to the shaft center pivot (25) is formed at the center of the piston through-hole (34) in the piston intermediate shaft (33). A piston pivot (35) is provided to pivotably pivot within a range of an angle (± θ) with respect to the rotating main shaft (20) on the axis (X), and the point (Ka) at both ends of the piston intermediate shaft (33). Hinge pin (51), (51) or hinge pin of hinge joint (50) element on point (Kb) side (52), (5
2), and the arcuate surfaces (41), (41) and both arcuate surfaces (41), (41), (2) are provided on both sides of the intermediate surface (33) of the piston on the axis (K) on the circular surface (S). 41), the piston intermediate shaft (3
3) An outer sliding contact surface (45) in which the chordal side surface (42) formed of a groove-shaped concave surface that is in sliding contact with the column surface and the back surfaces of both arcuate surfaces (41) and (41) are formed on the same rotation surface. An annular swash plate (40) is formed by combining an annular swash plate ring (43) rotatably fitted in the raceway gap (12) with the circular plate formed from the above and forming an outer peripheral surface. The skew plate (40) is provided with connecting elements corresponding to the hinge joint (50) elements on both sides of the skew plate ring (43) located on the point (Ka) point (Kb) side. The hinge joint (50) is fitted and the swash plate (40) and the rotating piston (3)
0) and the angle (± θ) with the dividing line (K) as the axis of the hinge
An element composition comprising a rotating piston (30), a swash plate (40), and a rotating main shaft (20) in a housing (10) constructed as described above is slidably connected to a range, and is composed of one set. Another similar to the ingredients
A set is formed and the two sets of compositions are connected in parallel or in series with each other so as to be interlocked. Then, the oblique plates (40) on both circular surfaces (S), (S),
(40) closes the inner wall surfaces of the housing (10) forming the spherical surfaces (G) and (G) given to each other to form semi-lunar working chambers (Ha) and (Ha) each having a hemispherical space. Each of the half-moon-shaped working chambers (Ha) and (Ha) is connected to a corresponding one of the rotating pistons (30) and (3) on the respective circular surfaces (R) and (R).
0) are two working chambers (Fu) forming a comb-shaped space,
(Fu), (Fu), and (Fu), and further, facing the semi-lunar working chambers (Ha) and (Ha), the working medium suction holes (In) and the discharge holes (Ex), and the working medium as appropriate. A spherical rotary piston engine provided with a valve device (Va) for opening and closing the passage of (1) and inserting an igniter (Ig) or a fuel injection valve into the combustion chamber.