JP3404571B2 - Spherical rotating piston engine - Google Patents

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a rotary piston 30 and a skew plate 40 in a housing 10 having a sliding spherical surface.
(Or housing skew plate 61) and a pair of rotary plates are incorporated, and the plate surfaces are moved toward and away from each other with the rotation so that intake, compression, expansion, and exhaust strokes in the internal combustion piston engine can be performed. The gas pressure of the expansion work is performed and the rotating piston 30
The present invention relates to a novel rotary piston engine that receives a plate surface of the rotary piston 30, converts it into a rotational force of the rotary piston 30, and rotates an output shaft connected to the rotary piston 30, has a very high piston speed, is lightweight, is compact, and has a high output. .

[0002]

2. Description of the Related Art At present, as a prime mover of a two-stroke cycle or a four-stroke cycle, a spark ignition engine of a reciprocating piston engine (hereinafter referred to as a reciprocating piston engine) and a diesel engine exist as various general-purpose engines. Further, as a small gasoline automobile engine of about 50 to 100 ps, which is a very small portion, there is a four-stroke cycle Wankel engine that combines the envelope of the 2-section epitrochoid curve and its inner envelope.

A reciprocating piston engine is composed of main components such as a cylinder and a piston, a connecting rod (connecting rod), a crankshaft, a flywheel (flywheel), and the piston head receives expansion pressure due to combustion of a medium in the cylinder. The piston converts the thermal energy into reciprocating motion as linear motion of mechanical energy, and the reciprocating motion is transmitted to the connecting rod through the piston pin, and the crankshaft connected to the connecting rod circles the linear reciprocating motion of the piston. It is converted into movement. Therefore, in the operation, a failure occurs due to the inertial mass of the reciprocating parts such as the piston, the connecting lot, and the valve. That is, the malfunction of the reciprocating piston engine results from the fact that the piston reciprocates linearly in the cylinder. That is, the reciprocating acceleration motion of the piston which is periodically repeated impairs the balance of the inertial force of the reciprocating mass and the inertia couple, so that the engine vibration is generated.

Further, it is necessary to use a multi-cylinder engine in order to reduce the inertial mass, increase in output and torque fluctuation. Inevitably, the multi-cylinder engine has a large volume, such as weight and size, as a whole. Since each piston is connected to the rotary shaft through the piston pin, connecting lot, and crank, the number of identical parts is increased. In addition, the intake / exhaust valve is attached to the top of the cylindrical cylinder, which limits the intake air weight, and
The tendency to increase the number of valves for improving the exhaust efficiency and reducing the inertial mass of the valve operating device is disadvantageous in disassembly and assembly workability and the number of parts. Or, in the same internal combustion engine, the reciprocating piston engine converts static pressure into rotational force in response to the dynamic pressure of the gas turbine, and since the volume / area ratio is small, the maximum combustion temperature is high and the harmful exhaust gas, nitrogen oxidation. Thing (NO
x) is often generated.

Further, the piston speed of the reciprocating piston engine can be increased as the stroke length in the stroke / inner diameter ratio becomes smaller. However, if it is too fast, it becomes difficult to follow the lubrication, and the engine is more likely to be damaged than the piston. Therefore, the vibration and noise due to the increase in the inertial mass of the piston slap and the reciprocating motion described above also increase. Similarly, the valve device also causes abnormal vibration as the engine speed increases to prevent the engine from rotating at a high speed, thereby narrowing the practical rotation range of the average piston speed. From the above, the disadvantage of the reciprocating piston engine is that the obstacle due to the inertial mass of the reciprocating motion part is unavoidable, the high rotation for high output is prevented, the operating rotation range is narrow, and the engine vibration and noise are generated. It is large, has a complicated structure, has a large engine volume, and produces a large amount of nitrogen oxides (NOx) that are difficult to purify.

Further, the Wankel engine is a triangular rotor housing having a two-node epitrochoid inner peripheral surface, and a triangular shape having three sides of an arcuate contour surface formed by the inner envelope of the two-node epitrochoid. Is provided with a rotor bearing having a circular hole passing through the central portion and a trochoidal phase gear having an internal gear mounted in the circular hole. In addition, the rod-shaped sealing elements attached to each vertex of the triangular rotor come into contact with the inner peripheral surface of the rotor housing,
Three working chambers are formed by the inner peripheral surface, the arcuate contour surface of the rotor, and the wall surfaces of the side housings that cover both sides, and the rotor is a fixed external tooth gear attached to the side housing that meshes with the trochoidal phase gear. The apex always rotates along the epitrochoidal curve of the rotor housing and revolves around a planetary motion.

The disadvantage of this Wankel engine is that the working chamber consisting of the housing and the rotor is composed of a flat surface or a flat plate, and the intake portion and the combustion portion are not at the same location. That is, the high temperature combustion chamber wall is not cooled by the fresh intake air, and the temperature difference between the intake side and the combustion side of the engine is large, and it is possible to follow the wall that is thermally deformed like a bimetal with an apex seal at the rotor apex. Absent. In addition, the working chamber has a rectangular cross section, and it is impossible to maintain the airtightness completely due to the change of the cross-sectional area, and there is a remarkable leakage and a significant friction wear due to the inability to generate an oil film for oil film lubrication.

Naturally, they show an increase and a deterioration in the consumption rate of fuel and lubricating oil in combination with the problems in principle.
The HC value, which is a cause of harmful CO and oxidant, so-called photochemical smog, is extremely increased by the forced discharge of unburned gas due to incomplete combustion, blow-through, dilution gas, and poor flame propagation. In addition, the parts and mechanism are difficult to understand due to lack of simplicity, require less manufacturing error and high assembly accuracy, cost is high and durability is inferior. not compatible.

[0009]

Therefore, the present invention has been made in view of the above-mentioned limitations and problems of the conventional internal combustion piston engine.
The conventional internal combustion piston engine is capable of satisfying various conditions essential to the internal combustion engine, such as output, fuel consumption, exhaust gas, quietness, durability, weight size, production cost, etc. Has a completely different basic structure from
The present invention also provides a new internal combustion piston engine having various performances superior to those of conventional engines.

[0010]

SUMMARY OF THE INVENTION The present invention has a basic structural feature that is established on a geometrical figure of interrelated points, lines, and surfaces. Further, the present invention has eight kinds of solving means showing a difference in basic structure in order to solve the above problems, and three kinds (common solving means 1 to 3) are provided for each of the eight solving means. There are possible forms of implementation.

[0011]

As a first means for solving the above problems, the present invention has a spherical surface G having a radius r with the spherical center O as the center of the housing 10 and having an angle θ and intersecting at the spherical center O. Let each of the two straight lines be the X-axis line and the Y-axis line.
The point where the axis intersects the spherical surface G is P, and the Y axis is the spherical surface G.
Is Q, the point P is between the points Q and the bottom is the diameter of the bottom surface, and the conical locus is the conical locus U with the spherical center O as the apex, and the points P and Q are half the bottom diameter. A conical locus having an apex at O is a conical locus J, and an axis line orthogonal to the X axis at the spherical center O is an M axis, and X
It is formed by passing through a ball center O in the spherical surface G with a great circle plane in the spherical surface G having a horizontal plane as its axis and having the axis L of its diameter segment as the axis of rotation, and the Y axis as the vertical axis. The great circle plane is the S circle surface, and the R circle surface and the S circle surface intersect at the spherical center O, and the intersecting secant forming the perpendicular line of the M axis line is the axis line K.
Then, both ends of the intersection secant K are defined as points Ka and Kb.

In the housing 10 in which the respective relations of points, lines, and surfaces are set as described above, a raceway gap 12 cut into a groove surrounding the inner wall portion of the housing 10 along the extension plane of the S circle surface, A shaft plate chamber 15 in which both opposing walls on the Y axis are cut out in a circular recess is provided outside the spherical surface G, and a main bearing 13 is provided at the center of the side wall of each shaft plate chamber 15. In both the main bearings 13, a shaft bar 24 rotatably housed in each of the shaft chambers 15 is connected to a connecting rod 26 on the X-axis to form a Z-shaped double shaft neck of a Z-axis 23. A tubular rolling shaft 72 is fitted onto the connecting rod 26, and a central portion of the rolling shaft 72 has an axial center 74 formed of a circular body of a pin joint joint 55 having the M axis as a connecting shaft.

On the R circular surface, there is a spherical arc surface 32 of an outer peripheral surface which is in sliding contact with the spherical surface G, and an arcuate surface 31 which forms an arcuate contour plane of the spherical arc surface 32 and has a chord on the K axis side. Further, a substantially plate-shaped rotary piston 30 in which a cylindrical piston intermediate shaft 33 is united is arranged on the chord side of the arcuate surface 31 with the rolling shaft 72 inserted. A piston center 35 for receiving the circular body of the shaft center 74 is formed at the center of the inside of the rotary piston 30, and the piston center 35 is used as the center center 74 with the rolling axis 72 on the X axis as the base axis and an angle θ × 2. Is pivotally attached in a range of
On the side of a and the point Kb, either the pin of the hinge joint 50 having the intersection secant K as the joint base axis or the connecting element including the pin receiving hole is provided.

On the S circle surface, there is an arcuate surface 41, an arcuate contour surface of the arcuate surface 41, and a chordal side surface 42, and the inner peripheral surface side is fixed to the arcuate contour surface to form an integral structure. Circular plate-shaped skew plate 4 formed with an annular skew plate ring 43 as an outer peripheral surface
Place 0. The slanting plate ring 43 of the slanting plate 40 is rotatably fitted in the orbital space 12, and the hinge joint 50 is provided at the facing portion located at the points Ka and Kb of the slanting plate ring 43.
When a connecting element corresponding to the element is provided and fitted, the skew plate 40 and the rotary piston 30 are connected so as to be slidable in an angle θ × 2 range with the intersecting secant K as the hinge axis.

In addition, the peripheral wall of the shaft plate chamber 15 is engraved on the fixed phase gear 14 of the fixed gear, and the rolling gear 76 of the external gear is provided at the end of the rolling shaft 72 to mesh with the fixed phase gear 14. . Then, the oblique plate 40 on the S circle surface closes the inner concave surface forming the spherical surface G in the housing 10 to form the half moon-shaped working chamber Ha in the hemispherical space, and the half moon shaped working chamber Ha is formed on the R circle surface. The rotary piston 30 is formed in the comb-shaped working chamber Fu forming a comb-shaped space. Further, a spherical rotation characterized in that an intake hole In and an exhaust hole Ex are provided so as to face the comb-shaped working chamber Fu, and an ignition tool Ig or a fuel injection valve is inserted into the combustion chamber by inspection. It is a piston engine.

[0016]

As a second solution, a spherical center O, a radius r, a spherical surface G, an angle θ, an axis X, an axis Y, a point P, and a point Q are provided inside the housing 10 as in the case of the above solution 1. Conical locus U, conical locus J, axis M, axis L, R circular surface, S circular surface, intersecting secant K, point Ka, point Kb, line, surface are set.

In the housing 10 in which the respective relationships of points, lines, and planes are set in this way, orbital gaps 12 cut into grooves surrounding the inner wall of the housing 10 along the extension plane of the S-circle, and Y A shaft plate chamber 15 in which both opposing walls on the axis are cut out in a circular recess is provided outside the spherical surface G, and a main bearing 13 is provided at the center of the side wall of each shaft plate chamber 15. A shaft bar 24, which is rotatably fitted in each of the shaft plate chambers 15, is connected to both main bearings 13 by a connecting rod 26 on the X axis to form a Z-shaped double shaft neck of a Z shaft 23. The shaft is supported, and a pivot connector 88 composed of a circular body element of a pin joint joint 55 having the M axis as a connecting shaft is attached to the central portion of the connecting rod 26 located at the spherical center O of the Z axis 23.

On the R circular surface, there are provided an outer peripheral spherical arc surface 32 which is in sliding contact with the spherical surface G, and an arcuate surface 31 which forms an arcuate contour plane of the spherical arc surface 32 and has the K axis side as a chord. Further, a substantially plate-shaped rotary piston 30 in which a cylindrical piston intermediate shaft 33 is united on the chord side of the arcuate surface 31 is arranged by inserting the connecting rod 26 of the Z-axis 23. This rotating piston 3
A piston pivot 35 for receiving the circular body element of the pivot connector 88 is formed in the inner center of 0, and the piston pivot 35 is pivoted on the pivot connector 88 in the range of an angle θ × 2 with the connecting rod 26 on the X axis as the base axis. A pin of the hinge joint 50 having a joint base axis of the intersecting secant K or a connecting element composed of a pin receiving hole is provided on the ends of the piston intermediate shaft 33 so as to be movably pivotally attached.

Further, on the S circle surface, there is an arcuate surface 41, an arcuate contour surface of the arcuate surface 41 and a chordal side surface 42, and the inner peripheral surface side is fixed to the arcuate contour surface to form an integral structure. Circular plate-shaped skew plate 40 formed with an annular skew plate ring 43 as the outer circumference
To place. The slanting plate ring 43 is rotatably fitted in the raceway gap 12, and the points Ka and Kb of the slanting plate ring 43 are arranged.
When a connecting element corresponding to the connecting element of the hinge joint 50 is provided and fitted in the facing portion located at, the skew plate 40 and the rotary piston 30 make the angle θ × 2 with the intersecting secant K as the axis of hinge attachment. The ranges are connected slidably.

In addition, the Z-axis 23-axis neck has an external gear Z
The shaft gear 27 is mounted, the circumference of the edge of the skew plate ring 43 is also engraved on the skew plate ring gear 44, and the intermediate gear 54 meshes with them.
Intervene. Then, the oblique plate 40 on the S circle surface closes the inner concave surface forming the spherical surface G in the housing 10 to form the half-moon-shaped working chamber Ha in the hemispherical space, and the half-moon-shaped working chamber Ha.
Is formed in the comb-shaped working chamber Fu in which the rotary piston 30 on the R circular surface forms a comb-shaped space. Furthermore, the comb-shaped working chamber Fu
The spherical rotary piston engine is characterized in that an intake hole In and an exhaust hole Ex are provided facing each other, and an ignition tool Ig or a fuel injection valve is inserted and attached by checking the combustion chamber.

[0021]

As a third solution, a ball center O, a radius r, a spherical surface G, an angle θ, an axis X, an axis Y, a point P, and a point Q are provided inside the housing 10 as in the case of the solution 1. Conical locus U, conical locus J, axis M, axis L, R circular surface, S circular surface, intersecting secant K, point Ka, point Kb, line, surface are set.

In the housing 10 in which the respective relationships of points, lines, and surfaces are set in this way, the inner wall surface of the housing 10 is formed as the inner wall surface forming the spherical surface G, and the inner wall surface along the extension plane of the S circle surface is formed. A raceway gap 12 of a groove that surrounds the portion is cut, and a main bearing 13 is provided through both opposing walls on the Y axis.
The two main bearings 13 each have a shaft arm 25 of an arbitrary shape connected by a connecting rod 26 on the X-axis to support a Z-shaped Z-axis 23 shaft neck. At the center of the connecting rod 26 located at the center O, a pivot connector 88 made of a circular body element of a pin joint joint 55 having an M axis as a connecting axis is attached.

On the R circular surface, a spherical arc surface 32 of the outer peripheral surface which is in sliding contact with the spherical surface G and an arcuate contour plane of the spherical arc surface 32 are formed to form K.
A substantially plate-shaped rotary piston 30 having an arcuate surface 31 having an axial line as a chord and having a cylindrical piston intermediate shaft 33 joined to the chordal side of the arcuate surface 31 is a shaft arm 25 and a connecting rod 26.
And the Z-axis 23 is inserted through the intermediate portion of the Z-axis 23. A piston pivot 35 for receiving the circular body element of the pivot connector 88 is formed at the center of the inside of the rotary piston 30. The range is pivotally attached so that the range is swingable, and the secant line K is provided on both ends of the piston intermediate shaft 33 at the points Ka and Kb.
A connecting element composed of a pin or a pin receiving hole of the hinge joint 50 having a joint base axis.

Further, on the S circle surface, there is an arcuate surface 41, an arcuate contour surface of the arcuate surface 41 and a chordal side surface 42, and the inner peripheral surface side is fixed to the arcuate contour surface to form an integral structure. Circular plate-shaped skew plate 4 formed with an annular skew plate ring 43 as an outer peripheral surface
Place 0. The slanting plate ring 43 is rotatably fitted in the raceway gap 12, and the points Ka and K of the slanting plate ring 43.
When a connecting element corresponding to the connecting element of the hinge joint 50 is provided and fitted in the facing portion located at b, the oblique plate 40 and the rotary piston 30 make the angle θ × with the intersecting secant K as the hinge axis. Connect the two ranges so that they can slide.

In addition, the Z-axis 23-axis neck has a Z-shaped external gear.
The shaft gear 27 is mounted, the circumference of the edge of the skew plate ring 43 is also engraved on the skew plate ring gear 44, and the intermediate gear 54 meshes with them.
Intervene. Then, the oblique plate 40 on the S-circular surface becomes the spherical surface G
The concave inner wall 11 of the housing 10 is closed to form a hemispherical working chamber Ha having a hemispherical space.
A is formed in the comb-shaped working chamber Fu in which the rotary piston 30 on the R circular surface forms a comb-shaped space. Furthermore, the comb-shaped working chamber F
The spherical rotary piston engine is characterized in that an intake hole In and an exhaust hole Ex are provided so as to face u, and an ignition tool Ig or a fuel injection valve is inserted and attached to the combustion chamber.

[0026]

As a fourth solution, a ball center O, a radius r, a spherical surface G, an angle θ, an axis X, an axis Y, a point P, and a point Q are provided inside the housing 10 as in the solution 1. Conical locus U, conical locus J, axis M, axis L, R circular surface, S circular surface, intersecting secant K, point Ka, point Kb, line, surface are set.

In the housing 10 in which the respective relationships of points, lines, and surfaces are set in this way, the inner wall surface of the housing 10 is formed into a spherical surface larger than the spherical surface G concentric spherical surface G, and X
A main bearing 13 is provided so as to extend through the axially opposed wall of the housing 10. The two main bearings 13 include a rotary spindle 20 having a straight shaft shape.
The shaft central shaft 21 is formed by a circular body of a pin joint joint 55 having the M axis as a connecting axis at the central portion of the rotary main shaft 20 which is located at the spherical center O of the rotary main shaft 20.

On the R-circular surface, there are provided an outer peripheral spherical arc surface 32 which is in sliding contact with the spherical surface G, and an arcuate surface 31 which forms an arcuate contour plane of the spherical arc surface 32 and has a chord on the K axis side. Further, a substantially plate-shaped rotary piston 30 in which a cylindrical piston intermediate shaft 33 is united on the chord side of the arcuate surface 31 is arranged with the rotary main shaft 20 being loosely inserted. A piston center 35 for receiving the circular body of the shaft center 21 is formed in the center of the inside of the rotary piston 30, and the piston center 35 is used as the center center 21 of the rotary main shaft 20 on the X-axis to form an angle θ × 2. Is pivotally attached in the range of the above-mentioned range, and the point K at both ends of the piston intermediate shaft 33 is
a, a connecting element composed of a pin of the hinge joint 50 or a pin receiving hole having the intersection secant K as the base axis of the joint is provided on the side of the point Kb.

On the S circle surface, there is an arcuate surface 41, an arcuate contour surface of the arcuate surface 41 and a chordal side surface 42, and the inner peripheral surface side is connected to the arcuate contour surface in an integral structure to form a housing. 1
A circular plate-shaped skew plate 40 formed with an annular skew plate ring 43 rotatably engaged with the 0 inner wall surface as an outer peripheral surface is arranged,
Incidentally, when a connecting element corresponding to the connecting element of the hinge joint 50 is provided and fitted at opposing portions located at the points Ka and Kb of the slanting plate ring 43, the slanting plate 40 and the rotary piston 3 are fitted.
0 connects the crossing secant K so as to be slidable in the range of the angle θ × 2 with the axis of the hinge.

A phase plate 56, which is a concave plate having an inner surface of a spherical surface G, is incorporated on each of both sides of the skew plate ring 43, and each of the phase plates 56 has a phase plate bearing 57 penetrating on the point P. Is provided and the rotary spindle 20 is fitted therein. Furthermore, the phase plate gear 58 of the external bevel gear is attached to the outer surface of the phase plate 56 around the hole of the phase plate bearing 57, and the main shaft gear 22 of the external bevel gear is also attached to the shaft neck of the rotary main shaft 20. In addition, the intermediate gear 54 that meshes with them is interposed. Then, the oblique plate 40 on the S circle surface closes the inner concave surface forming the spherical surface G in the housing 10 to form the half-moon-shaped working chamber Ha of the hemispherical space,
The half-moon-shaped working chamber Ha is formed in the comb-shaped working chamber Fu in which the rotary piston 30 on the R circular surface forms a comb-shaped space. Furthermore,
The suction hole In and the discharge hole E are made to face the comb-shaped working chamber Fu.
x is provided and an ignition tool Ig or a fuel injection valve is inserted and attached by checking the combustion chamber, and is a spherical rotary piston engine.

[0031]

As a fifth solution, a ball center O, a radius r, a spherical surface G, an angle θ, an axis X, an axis Y, a point P, and a point Q are provided inside the housing 10 as in the case of the solution 1. Conical locus U, conical locus J, axis M, axis L, R circular surface, S circular surface, intersecting secant K, point Ka, point Kb, line, surface are set.

In the housing 10 in which the respective relations of points, lines, and surfaces are set in this way, the inner wall surface of the housing 10 is formed as a rotation surface larger than a spherical surface G concentric with the Y axis and Y is formed.
The main bearing 13 is pierced through the opposite wall of the housing 10 on the axis,
In the housing 10, a spherical Z-axis housing 70 having an inner side surface forming a spherical surface G and a handle-shaped housing shaft 71 that is axially fixed on opposite sides on the Y-axis is rotatably fitted to the housing shaft 7.
1 is supported on the main bearing 13. In this Z-axis housing 70,
An orbital gap 87 formed in a groove that circulates a portion of an inner surface along an extension plane of the S-circle and rolling bearings 73 provided on both sides facing each other on the X axis are provided, and the rolling bearing 73 has a straight-axis rolling shape. It has both axial necks of the shaft 72, and has an axial center 74 composed of a circular body of a pin joint joint 55 located at the spherical center O of the rolling shaft 72 and having the M axis as a connecting shaft.

On the R circular surface inside the Z-axis housing 70, a spherical arc surface 32 of an outer peripheral surface which is in sliding contact with 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. Bow surface 31
And a substantially plate-shaped rotary piston 30 having a cylindrical piston intermediate shaft 33 united with the arcuate surface 31 on the chord side thereof is disposed with the rolling shaft 72 loosely inserted. A piston center 35 for receiving the circular body of the shaft center 74 is formed at the center of the inside of the rotary piston 30, and the piston center 35 is used as the center center 74 with the rolling axis 72 on the X-axis as the base axis.
From the pin of the hinge joint 50 or the pin receiving hole which pivotally supports the range of × 2 and pivots on both ends of the piston intermediate shaft 33 at the points Ka and Kb with the intersecting secant K as the base axis of the joint. A connecting element is provided.

Then, on the S circle surface in the Z-axis housing 70,
The arcuate surface 41, the arcuate contour surface of the arcuate surface 41, and the chord side surface 42.
And a circular plate having an arcuate contour surface, the inner peripheral surface side of which is integrally connected, and which is rotatably engaged with the track gap 87 of the Z-axis housing 70 as an outer peripheral surface. When a slanting plate 40 is arranged, and a connecting element corresponding to the connecting element of the hinge joint 50 is provided and fitted at opposing portions of the slanting plate ring 43 located at points Ka and Kb, the slanting plate 40 is slanted. Board 40
And the rotary piston 30 slidably connects the angle θ × 2 range with the intersecting secant K as the hinge axis.

In addition, fixed phase gears 14 of gears fixed to opposite walls in the housing 10 sandwiching the S circle surface are engraved concentrically with the Y axis, and the rolling shaft 72 has a neck end portion of an external gear. A rolling gear 76 is provided to mesh with the fixed phase gear 14. Then, the oblique plate 40 on the S-circle closes the inner concave surface of the Z-axis housing 70 forming the spherical surface G to form the half-moon-shaped working chamber Ha in the hemispherical space, and the half-moon-shaped working chamber Ha is formed into the R-circular surface. The upper rotary piston 30 forms a comb-shaped working chamber Fu that forms a comb-shaped space. Further, a spherical rotation characterized in that an intake hole In and an exhaust hole Ex are provided so as to face the comb-shaped working chamber Fu, and an ignition tool Ig or a fuel injection valve is inserted into the combustion chamber by inspection. It is a piston engine.

[0036]

As a sixth solution, a spherical center O, a radius r, a spherical surface G, an angle θ, an axis X, an axis Y, a point P, and a point Q are provided inside the housing 10 as in the case of the above solution 1. Conical locus U, conical locus J, axis M, axis L, R circular surface, S circular surface, intersecting secant K, point Ka, point Kb, line, surface are set.

In the housing 10 in which the respective relationships of points, lines, and surfaces are set in this way, the inner wall surface of the housing 10 is formed as a spherical G concentric surface or a rotation surface larger than the Y-axis concentric spherical surface G and on the Y-axis. A main bearing 13 is provided on a wall opposite to the housing 10, and the housing 10 has an inner side surface forming a spherical surface G, and a partition plate-shaped housing skew plate 61 and S on the S circular surface of the inner side surface. A spherical housing 60 having a shaft plate chamber 64, which is formed by cutting out circular recesses on opposing surfaces sandwiching a circular surface, and a housing bearing 63 at the center of a side wall of the shaft plate chamber 64, is rotatably fitted to a spherical housing 60. Is incorporated as the axis of rotation. Further, in the main bearing 13 and the housing bearing 63 on both sides, each of the shaft plates 24 rotatably fitted in each of the shaft plate chambers 64 is connected by a connecting rod 26 on the X axis to form a Z-shaped Z axis. A connecting rod 26 that supports both shaft necks of 23 and is located at the spherical center O of the Z axis 23.
A pivot connector 88 formed of a circular body element of the pin joint joint 55 having the M axis as a connecting shaft is fitted on the central portion of the.

On the R circular surface inside the casing 60, a spherical arc surface 32 of an outer peripheral surface which is in sliding contact with the inner surface of the housing 60 forming a spherical surface G, and an arcuate contour plane of the spherical arc surface 32 are formed, and The connecting rod of the Z-axis 23 is a substantially plate-shaped rotary piston 30 that has an arcuate surface 31 having a chord on the axis side, and a cylindrical piston intermediate shaft 33 is integrated on the chord side of the arcuate surface 31. 26 is inserted and arranged. In the center of the inside of the rotary piston 30, a piston pivot 3 for receiving the circular body element of the pivot connector 88 is provided.
5, the piston pivot 35 is pivotally attached to the pivot connector 88 so as to be swingable in the range of the angle θ × 2 with the connecting rod 26 on the X-axis as the base axis, and the points K on both ends of the piston intermediate shaft 33.
a, a connecting element composed of a pin of the hinge joint 50 or a pin receiving hole having the intersection secant K as the base axis of the joint is provided on the side of the point Kb.

Then, on the S-circular surface in the housing 60, the housing slanting plate 61 having an arcuate surface 41, an arcuate contour surface of the arcuate surface 41, and a chordal side surface 42, is formed by housing the arcuate contour surface. 6
When it is fixedly attached to the inner surface of 0 and is formed as an integral structure, a connecting element corresponding to the connecting element of the hinge joint 50 is provided and fitted to the opposing portion located on the side of the points Ka and Kb of the housing 60. An angle θ × 2 between the skewed plate 61 of the casing in the casing 60 and the rotary piston 30 with the intersecting secant K as the axis of the hinge.
The ranges are connected slidably.

In addition, the external gear bevel gear housing gear 62 mounted on the outer surface of the housing 60 around the housing bearing 63 hole, and Z
The shaft 23 has a Z-axis gear 27, which is an externally toothed bevel gear attached to the shaft neck, and an intermediate gear 54 meshing with them is interposed.
Then, the housing oblique plate 61 on the S-circle closes the inner concave surface forming the spherical surface G in the housing 60 to form the half-moon-shaped working chamber Ha in the hemispherical space, and the half-moon-shaped working chamber Ha is formed into the R-circular surface. The upper rotary piston 30 forms a comb-shaped working chamber Fu that forms a comb-shaped space. Further, a spherical rotation characterized in that an intake hole In and an exhaust hole Ex are provided so as to face the comb-shaped working chamber Fu, and an ignition tool Ig or a fuel injection valve is inserted into the combustion chamber by inspection. It is a piston engine.

[0041]

As a seventh solution, a ball center O, a radius r, a spherical surface G, an angle θ, an axis X, an axis Y, a point P, and a point Q are provided inside the housing 10 as in the case of the solution 1. Conical locus U, conical locus J, axis M, axis L, R circular surface, S circular surface, intersecting secant K, point Ka, point Kb, line, surface are set.

In the housing 10 in which the respective relationships of points, lines, and surfaces are set in this way, the inner wall surface of the housing 10 is formed as a spherical G concentric surface or a rotational surface larger than the Y-axis concentric spherical surface G and on the Y-axis. Is provided with a main bearing 13 on a wall facing the housing 10, and the housing 10 has an inner side surface that forms a spherical surface G, and a partition plate-like skewed board 61 on the S circular surface of the inner side surface, and Y. A spherical housing 60 having rotatably fitted housing bearings 63 on opposite sides through which the axis passes.
Is incorporated with the Y axis as the axis of rotation. Further, the main bearing 13 and the housing bearing 63 on both sides are provided with the shaft arm 25 having an arbitrary shape.
The connecting rods 26 on the X-axis are connected to each other to support both necks of the Z-axis 23 of the Z-axis 23, and the M-axis is attached to the central portion of the connecting rod 26 located at the spherical center O of the Z-axis 23. A pivot connector 88, which is a circular body element of the pin joint joint 55 serving as a connecting shaft, is externally fitted.

On the R circular surface inside the housing 60, a spherical arc surface 32 of the outer peripheral surface which is in sliding contact with the inner surface of the housing 60 forming the spherical surface G and an arcuate contour plane of the spherical arc surface 32 are formed, and the K A substantially plate-shaped rotary piston 30 having an arcuate surface 31 having a chord on the axis side and having a cylindrical piston intermediate shaft 33 joined to the chord side of the arcuate surface 31 is the shaft arm 25 and the connecting rod. An intermediate portion of Z axis 23 with respect to 26 is inserted and arranged. A piston center 35 for receiving the circular body element of the pivot connector 88 is formed in the center of the inside of the rotary piston 30, and the piston center 3 is formed.
5 is pivotally attached to the pivot 88 so as to be swingable in the range of the angle θ × 2 with the connecting rod 26 on the X-axis as the base axis, and the intersection secant K is provided on both ends of the piston intermediate shaft 33 at the points Ka and Kb. A pin of the hinge joint 50, which is the base axis of the joint, or a connecting element composed of a pin receiving hole is provided.

On the S-circle inside the housing 60, the above-mentioned housing slanting plate 61 having an arcuate surface 41, an arcuate contour surface of the arcuate surface 41, and a chordal side surface 42, is formed by housing the arcuate contour surface. 6
When it is fixedly attached to the inner surface of 0 and is formed as an integral structure, a connecting element corresponding to the connecting element of the hinge joint 50 is provided and fitted to the opposing portion located on the side of the points Ka and Kb of the housing 60. An angle θ × 2 between the skewed plate 62 of the casing in the casing 60 and the rotary piston 30 with the intersecting secant K as the axis of the hinge.
The ranges are connected slidably.

In addition, an external bevel gear housing gear 62 mounted on the outer surface of the housing 60 centering on a housing bearing 63 hole, and Z.
The shaft 23 has a Z-axis gear 27, which is an externally toothed bevel gear attached to the shaft neck, and an intermediate gear 54 meshing with them is interposed.
Then, the skew board 61 on the S-circle closes the inner concave surface of the housing 60 forming the spherical surface G, and the half-moon-shaped working chamber H of the hemispherical space.
a is formed, and the half-moon-shaped working chamber Ha is formed into a comb-shaped working chamber Fu in which the rotary piston 30 on the R circular surface forms a comb-shaped space. Further, the suction hole I is made to face the comb-shaped working chamber Fu.
n and the discharge hole Ex are provided, and the ignition chamber I
g, or a spherical rotary piston engine having a fuel injection valve inserted therein.

[0046]

As an eighth solution, a ball center O, a radius r, a spherical surface G, an angle θ, an axis X, an axis Y, a point P, and a point Q are provided inside the housing 10 as in the solution 1. Conical locus U, conical locus J, axis M, axis L, R circular surface, S circular surface, intersecting secant K, point Ka, point Kb, line, surface are set.

In the housing 10 in which the respective relationships of points, lines, and surfaces are set in this way, the inner wall surface of the housing 10 is formed concentrically with the spherical surface G, or with a rotation surface larger than the spherical surface G concentric with the Y axis, and on the X axis. The main bearing 13 is provided on the opposite wall of the housing 10, and the inside surface of the housing 10 has a spherical surface G and is cut into a groove that encircles an inner portion along the extension plane of the S circle surface. A spherical phase housing 80 having a gap 87 and housing bearings 83 on opposite sides through which the X axis penetrates and rotatably fitted is incorporated with the X axis as the rotation axis. Further, the main bearing 13 and the housing bearing 83 on both sides support both shaft necks of the rotary spindle 20 having a straight shaft shape, and the M axis is connected to the connecting shaft with the central portion located at the ball center O of the rotary spindle 20. It has an axial center 21 which is a circular body of a pin joint joint 55.

On the R-circular surface in the phase housing 80, a spherical arc surface 32 of an outer peripheral surface which is in sliding contact with the inner surface of the phase housing 80 forming a spherical surface G and an arcuate contour plane of the spherical arc surface 32 are formed. K
A substantially plate-shaped rotary piston 30 having an arcuate surface 31 having a chord on the axis side and having a cylindrical piston intermediate shaft 33 united on the chord side of the arcuate surface 31 is inserted through the rotary main shaft 20. Will be placed. A piston center 35 for receiving the circular body of the shaft center 21 is formed in the center of the inside of the rotary piston 30, and the piston center 35 is used as the center center 21 of the rotary main shaft 20 on the X-axis to form an angle θ × 2. Of the hinge joint 50, which is pivotally attached in the range of ∘, and whose intersection secant K is the joint base axis on the points Ka and Kb at both ends of the piston intermediate shaft 33.
A connecting element consisting of a pin or a pin receiving hole is provided.

Then, on the S circle surface in the phase housing 80,
The arcuate surface 41, the arcuate contour surface of the arcuate surface 41, and the chord side surface 42.
A circular plate-shaped skew plate 40 having an annular skew plate ring 43 formed on the outer periphery and having an inner peripheral surface side fixed to the arcuate contour surface and having an integrated structure is disposed. The slanting plate ring 43 is rotatably fitted in the raceway gap 72, and the slanting plate ring 43 is
Of the hinge joint 5 at the facing portions located at points Ka and Kb of
When a connecting element corresponding to the connecting element of 0 is provided and fitted, the oblique plate 40 and the rotary piston 30 are connected so as to be slidable in the angle θ × 2 range with the intersecting secant K as the hinge axis.

In addition, the housing 8 is provided on the outer surface of the phase housing 80.
External gear bevel gear housing gear 82 mounted around three holes
And the main spindle gear 22 of the external bevel gear attached to the rotary main spindle 20 shaft neck, and the intermediate gear 54 meshing with them is interposed. Then, the oblique plate 40 on the S-circle closes the inner concave surface of the phase housing 80 forming the spherical surface G to form the half-moon-shaped working chamber Ha in the hemispherical space, and the half-moon-shaped working chamber Ha is located on the R-circle. The rotary piston 30 is formed in the comb-shaped working chamber Fu forming a comb-shaped space. Further, a spherical rotation characterized in that an intake hole In and an exhaust hole Ex are provided so as to face the comb-shaped working chamber Fu, and an ignition tool Ig or a fuel injection valve is inserted into the combustion chamber by inspection. It is a piston engine.

[0051]

[Common Solution Means 1] In the structure of the solution means 1 to 8, the rotary piston 30 has the spherical arc surface 3 on opposite sides thereof.
2, 32 and the arcuate surfaces 31, 31, 31, on both sides
31 is formed into a circular plate by interposing the piston intermediate shaft 33 on the chordal side surfaces of two arcuate plates having 31 and, and the oblique plates 40 on the S circular surface are formed on both sides inside the housing 10. The crescent-shaped working chambers Ha and Ha are formed by facing each other with concave surfaces forming a spherical surface G by separating the crooked plates 61 from each other or by separating the inside of the casing 60 on both sides. Each of Ha and Ha has the comb-shaped working chamber Fu, Fu in which two rotary pistons 30 on the R circular surface are provided,
Formed on Fu and Fu.

[0052]

[Common Solution Means 2] Alternatively, in the configuration of the solution means 1 to 8, the rotary piston 30 is provided on both sides on the same plane sandwiching the K-axis with the spherical arc surface 32 larger than a hemispherical surface straddling the S circle surface. The arcuate surfaces 31 and 31 are formed into a semi-spherical substantially circular plate by interposing the piston intermediate shaft 33 between the arcuate surfaces 31 and 31, and the oblique plate on the S circular surface is formed. 40 divides the inside of the housing 10 on both sides,
Alternatively, the skewed plate 61 of the housing divides the inside of the housing 60 on both sides to form the half-moon-shaped working chambers Ha, Ha in which concave surfaces forming a spherical surface G face each other, and the half-moon-shaped working chamber Ha,
The rotating pistons 30 on the R-circle form the respective Has in the comb-shaped working chambers Fu, Fu.

[0053]

[Common Solution Means 3] Alternatively, in the configuration of the solution means 1 to 8, the rotary piston 30 has the spherical arc surface 32 and the arcuate surface 3 on the front and back sides on either side of the K axis.
The piston intermediate shaft 33 is united with the chordal side of an arcuate plate having the numbers 1 and 31 to form a substantially semicircular plate, and the oblique plate 40 on the S circular surface forms a spherical surface G in the housing 10. The half-moon-shaped working chamber Ha is formed by sealing the concave surface or by sealing the concave surface forming the spherical surface G in the housing 60 by the diagonal plate 61 of the housing.
The rotary piston 30 on the circular surface has two comb-shaped working chambers F.
It is formed in u and Fu.

[0054]

Geometrical Structure The present invention has the characteristics and operating principle of the basic structure which is established on the geometrical structure of the geometrical structure of the points, lines and surfaces which are related to each other. Hereinafter, a structural principle and an operation mode on a geometrical figure will be described with reference to the drawings.

First, the relationship diagram defining the spherical rotary piston engine of the present invention is shown in FIG. 1 in the solving means 1 to 3 and the solving means 5 to 7, and in FIG. 18 in the solving means 4 and 8. As shown in FIG.
Has a spherical surface G with a radius r as the center of the X axis, forms an angle θ, and intersects two straight lines at the spherical center O with the X-axis line and the Y-axis line, respectively.
An axis is defined as a point, and a point where the X axis intersects the spherical surface G is defined as a point P,
The point where the Y axis intersects the spherical surface G is defined as point Q, and the point P,
A conical locus with a diameter of the bottom surface between the points Q and the apex of the spherical center O is defined as a conical locus U, and a point between the points P and Q is a half of the diameter of the bottom surface and a conical locus with the apex of the spherical center O is a conical shape. Trail J
And the axis line orthogonal to the X axis at the center O of the ball is M
A great circle plane within a spherical surface G having an axis line and a horizontal plane along the X axis line with the axis L of the diameter segment as the axis of rotation is the R circle surface, and the Y axis line is the vertical axis line. Let the great circle plane formed through the circle be an S circle, and the R circle and S
An axis K is defined as an intersecting secant that intersects the circle surface at the spherical center O and is perpendicular to the M axis, and both ends of the intersecting secant K are designated as points K.
a and a point Kb, and the respective relationships of the point, the line, and the surface are set in this way.

When the X-axis and the Y-axis in FIGS. 1 and 18 are both regarded as the localization axis at a fixed position, the X and Y axes are simultaneously rotated at the same speed and in the same direction.
The S-circle, which is the vertical plane of the axis, turns around the Y-axis as a rotation axis while maintaining its phase, but it intersects with the S-circle on the K-axis and the M-axis is connected to the X-axis. The R circular surface connected as a line is rotated so as to switch the front and back while reciprocating in the range of (θ × 2) on the X axis. That is, S
With the rotation of the circular surface, the rotation axis L of the R circular surface has a conical side surface whose conical generatrix has a conical side circumference with a spherical center O as an apex with a bottom diameter between points P and Q on the X and Y axes. It turns while rotating on the above-mentioned circular conical locus U.

The self of the R circle rotating on the conical locus U
When the revolution is the primary rotation Po, the rotation axis L of the R circular surface revolves a semicircle of the conical locus U from the X-axis line to the Y-axis line in the rotation of 90 ° of the rotation, and further 90 degrees. In the rotation of, the remaining semicircular locus of the conical locus U is drawn from the Y-axis line to return to the original X-axis line. That is, if the rotation axis L of the R circle surface revolves around the circumference of the conical locus U, the R circle surface will rotate by 180 degrees and the front and back will be changed in association with the one revolution. Further, when the rotation axis L of the R circular surface makes one revolution on the conical locus U and makes two revolutions, the R circular surface rotates for one rotation and returns the front and back sides.

The rotation axis L of the R circle surface and the intersecting secant K in the primary rotation Po are always orthogonal to each other at the spherical center O, and the gap between the intersecting R circle surface and S circle surface is the rotation axis L of the R circle surface. In the intersection angle of the R and S circles created when the X axis line overlaps, the maximum gap range (spaces B and D in FIGS. 1 and 18) is the vertical angle side of the obtuse angle having the (90 + θ) angle.
The minimum gap range (spaces A and C in FIG. 1 and FIG. 18) is on the side of the vertical angle of the acute angle having the (90−θ) angle, but the R circle surface and the S circle surface have the intersection secant K as the axis of the hinge. They approach each other by half a rotation and separate from each other by the next half rotation, and each time the rotation is repeated, the separation and engagement in which the pair approaches and separates is repeated.

Looking at the spaces A, B, C, and D enclosed by the spherical surface G, the R circular surface, and the S circular surface, the space A in FIG. 1 and FIG. Is expanded, the space C is contracted, and the space D is expanded. When the rotation progresses in the directions of FIGS. 2 and 3 and FIGS. 19 and 20, the space A expands and the space B contracts, and the space C expands and the space D expands.
Contracts. That is, when the space A expands, the space B contracts, and when the space C expands, the space D contracts. At the same time, the space D contracts as the space A expands, and the space C expands as the space B contracts. Have a relationship to Therefore, the spaces A and B are changed in inverse proportion to each other to form a pair, and the spaces C and D are also changed in inverse proportion to each other to be paired, and the spaces A and C and the spaces B and D are combined. Has the inverse relationship to the order in which the mutual volume changes are directly proportional.

Therefore, in the solving means 1 to 3 and the solving means 5 to 7 shown in FIGS. 1 to 13, the X axis is shown around the Y axis with the Y axis as the central axis, or in FIGS. 18 to 30. In the above solving means 4 and 8, the Y axis is X.
A secondary rotation Ne that turns on the conical locus J in the opposite direction of the primary rotation Po while maintaining the angle θ around the axis is provided at the same time as the primary rotation Po.
Then, according to the ratio of forward and reverse rotations that rotate in the reverse direction,
The secondary rotation Ne rotates one or more times including one rotation for one rotation of the primary rotation Po, or any one or more rotations including one rotation of the primary rotation Po for one rotation of the secondary rotation Ne. Whether or not it rotates the number of times, the conical locus U itself also rotates in the secondary rotation Ne direction.

Alternatively, in the solving means 1 to 3 and the solving means 5 to 7, the X axis is around the Y axis with the Y axis as the central axis, or in the solving means 4 and 8 is Y.
The secondary rotation Ne, which turns on the conical locus J in the same direction as the rotation direction of the primary rotation Po while keeping the angle θ around the X axis as the central axis, simultaneously with the primary rotation Po. give. Then, the primary and secondary rotations Po, which rotate in the same direction but have different rotational speeds,
Depending on the forward rotation ratio of Ne, the secondary rotation Ne rotates 3 times or more per one rotation of the primary rotation Po, or the primary rotation Po rotates 3 or more times per rotation of the secondary rotation Ne. Whether or not the minute is rotated, the conical locus U itself is also rotated in the secondary rotation Ne direction.

As described above, in the spherical rotary piston engine of the present invention, the primary rotation Po and the secondary rotation Ne rotate in the forward and reverse directions, and the primary rotation in confrontation with the forward and reverse rotation. There is a form of forward rotation in which Po and the secondary rotation Ne rotate in the same direction. In addition, in each of the normal rotation mode and the forward rotation mode, the speed ratio between the primary rotation Po and the secondary rotation Ne can be changed, but the rotation ratio of the secondary rotation Ne is the primary rotation Po. Higher forward / reverse rotation (forward / reverse rotation (form 6,
7 and embodiments 2, 3, and 4)], and the primary rotation Po
Of normal / reverse rotation having a higher rotation ratio than the secondary rotation Ne (forward / reverse rotation (Embodiments of forms 5 and 8 and forms 1, 2 and 4))
And a mode of forward rotation in which the primary rotation Po and the secondary rotation Ne rotate in the same direction [forward rotation (each embodiment of modes 1 to 8)]
Will be supplemented in the following description, and the primary rotation Po will be described below.
Will be described in detail based on the form of forward / reverse rotation in which the rotation ratio of the secondary rotation Ne is equal.

[0063]

[Operational principle 1 on geometrical figure] The operational principle 1 on geometrical figure is any one of the above-mentioned solving means 1, 2, 3, 5, 6, 7. In the above-described secondary rotation Ne that rotates in the opposite direction of the primary rotation Po, the Y axis is a localization axis that rotates at a fixed position as shown in FIGS.
The axis is a floating movable axis that orbits around the Y axis.

Therefore, according to the operating principle 1 on this geometrical figure, even if the forward and reverse rotation primary and secondary rotations Po and Ne are combined, the S circle surface having the Y axis as the rotation axis always rotates without changing the phase. Then, the R circle surface rotates in the horizontal direction on the X axis while repeating the range of (θ × 2). That is, the R circle surface rotates with respect to the S circle surface, and the separation is performed by the intersection secant K.
Is caused by the swing of the R circle surface with the S circle surface as the opposing surface of the swing movement, with the swing of the R circle surface as 2 of the R and S circle surfaces.
The gap existing between the surfaces is changed, and the change in the gap directly changes the volume of the spaces A, B, C, and D.

Explaining from the rotation of the X-axis based on the movement of the figure, the primary rotation P shown in FIG. 14 and FIG.
o rotates the M-axis line that crosses the X-axis line at the spherical center O in the direction of the arrow given to the X-axis line of FIG. Then, the R circular surface on the X axis centered on the vertical axis of the M axis is the spherical center O as the apex and the point P as the apex with the rotation axis L as the rotation axis in the order of FIG. , Q is rotated on a conical locus U having a bottom diameter between them, and as the R circle rotates, the S circle that intersects and intersects with the axis K interlocks with the rotation direction of the R circle with the Y axis as the rotation axis. . That is, the R-circle of the half circle rotates its own rotation axis L from the X-axis line shown in FIG. 14 (a) to (b) and (c), the Y-axis line shown in (d), and then (e), (F) and FIG. 15 (g), the circle on the conical locus U corresponding to the angle θ returning to the X-axis line is rotated once, and one rotation is 2θ.
2 laps per minute.

At that time, the R circle plane is located in the middle of the X axis plane and the S circle plane with the cross axis line of the M axis line and the K axis line orthogonal to each other.
The X axis and the S circle surface are linked and interlocked, but the rotation axis L of the R circle surface is on the X axis line when the K axis line is orthogonal to the X axis line as shown in FIG. ) As shown in Y
When the M axis is orthogonal to the axis, it is on the Y axis. After all,
The R circular surface makes a half rotation on the X-axis and reversely oscillates by an angle θ in the horizontal direction, and performs the above-described primary rotation Po that reciprocates within the 2θ range in one rotation. Further, the angle θ is an intersection angle formed on the acute angle side between the X and Y axis lines, and is also an open angle on the acute angle side between the rotation surface of the M axis line and the S circle surface due to the rotation of the X axis line.

Then, the secondary rotation which rotates in the opposite direction of the primary rotation Po with the Y axis as the axis of rotation for the whole of each relation with the R and S circles which make the primary rotation Po with the X axis as the reference. Ne is given simultaneously with the primary rotation Po. At that time, if the forward / reverse rotation ratio is set to, for example, 1: 1 (1/1 to the numerator indicate the forward rotation primary rotation Po, and the denominator indicates the secondary rotation Ne that is the reverse rotation), FIG. As shown in FIG. 15G, (90 degrees + θ) is shown in FIG. 15G after the R and S circles that perform the primary rotation Po as shown in FIG. The rotation angle position of the Y-axis line which should be the maximum gap of (4) is set in FIG. 7 which shows the forward and reverse rotations of the primary and secondary rotations Po and Ne, which are set back by 90 degrees from that of FIG.

That is, the primary rotation P with the Y axis as the axis of rotation
The secondary rotation Ne for reversing o changes the phase of the R circle surface but does not rotate the R circle surface, and the forward / reverse rotation ratio is 1: 1 (1 /
The gap between the R circle surface and the S circle surface is changed from the minimum to the maximum or from the maximum to the minimum every half rotation (180 degrees) in 1). Therefore, in the case of only the primary rotation Po, the change in the gap between the R and S circular surfaces is one reciprocation of 1 increment and decrement per revolution of the Y-axis, whereas it is shown in the order of FIG. 13 from FIG. 1 to FIG. 2 to FIG. As described above, when the secondary rotation Ne having the forward / reverse rotation ratio of 1: 1 (1/1) is added, the change in the gap between the R and S circles corresponds to one reciprocation for one half rotation of the Y axis. And, furthermore, the figure 1
When the Y-axis of 3 is rotated a half turn in the rotation direction, the gap between the R and S circular surfaces makes one reciprocation of 1 increase / decrease and returns to the original FIG.

That is, the change in the gap between the R and S circles in one rotation of the Y-axis including the secondary rotation Ne of the forward / reverse rotation ratio of 1: 1 (1/1) is 2 reciprocations of 2 increases and 2 decreases. . At that time, FIG. 1 showing the process of changing the gap between the R and S circular surfaces in the primary rotation Po.
FIGS. 4 (a) to (f) and FIGS. 15 (g) to 15 (w) show the process of changing the gap between the R and S circular surfaces in the combined rotation of the primary rotation Po and the secondary rotation Ne. 13 showing the forward and reverse rotation again corresponds to FIG. 14A of the primary rotation Po.

In the operating principle 1 on the geometrical figure in the present invention, the change in the gap between the R and S circular planes in the forward and reverse rotations is replaced with the stroke volume of the working chamber Fu, that is, the change in the volume of the so-called air chamber space. Rolling shaft 72 on the X-axis is set by increasing or decreasing the volume of each stroke of A, B, C, D.
(Solution 1, 5) or pivot 88 (Solution 2,
3, 6, 7) and the rotary piston 30 on the R and S circles that intersect on the piston intermediate shaft 33 on the K axis and the skew plate 4
0 (solving means 1, 2, 3, 5), or the diagonal board 61 of the housing
(Solutions 6, 7) are rotated, and Z-axis 23 on the Y-axis to be mounted as an output shaft (Solutions 1, 2, 3,
6, 7) or the housing shaft 71 (solution means 5) is to be rotated. In this case, (forward) in forward / reverse rotation is the rotary piston 30 that makes the primary rotation Po and the skew plate 40 (solving means 1, 2, 3, 5) or the rotary piston 3.
0 and rotation of the housing 60 (solving means 6, 7) are shown (inverse)
Is the Z-axis 23 that performs the secondary rotation Ne (solving means 1, 2, 3,
6, 7) or rotation of the Z-axis housing 70 (solution means 5).

[0071]

[Operating principle 2 on geometrical figure] The operating principle 2 on geometrical figure is any one of the constitutions of the solving means 4 and 8 described above, and the reverse rotation of the primary rotation Po in the operating principle 2 on this geometrical figure is performed. The secondary rotation Ne is a localization axis line in which the X axis line rotates at a fixed position, as shown in FIGS. 18 to 30,
With respect to the localization axis X, the Y axis is a floating movable axis that turns around the X axis as the central axis.

Therefore, the operating principle 2 on this geometrical figure is
If the primary rotation Po and the secondary rotation Ne that rotate in the reverse direction are combined, the S circle surface having the Y axis as the rotation axis in addition to the R circle surface also rotates while changing the phase, and the phase of the S circle surface With the change of, the R circle surface is separated from the S circle surface by repeating the range (θ × 2) in the horizontal direction on the X axis. That is, the separation of the R circle surface and the S circle surface is caused by the oscillating movement of the R circle surface with respect to the S circle surface having the intersection secant K as the axis of the hinge, and the oscillating movement of the R circle surface is the two surfaces of the R and S circle surfaces. The gap existing between them is changed, and the change in the gap between the R and S circular surfaces directly changes the volume of the spaces A, B, C, and D.

Explaining the movement of the figure from the primary rotation Po based on the rotation of the X axis shown in FIGS. 31 and 32, the rotation in the arrow direction given to the X axis of FIG. Rotate the M axis that intersects the X axis and the cross. Then, R on the X-axis centered on the M-axis
A circular surface rolls on the conical locus U having the spherical center O as the apex and the point P, Q as the bottom diameter with the axis of rotation L as the axis of rotation in the order of FIG. 31A to B). With the rotation of the R circle surface, the S circle surface that connects and intersects with the R circle surface at the axis K is rotationally interlocked about the Y axis. That is, the R circle surface is rotated by half its rotation about its own rotation axis L from the X-axis line shown in FIG. 31 (a) to (b) and (c), the Y-axis line shown in (d), and then (e) (F) and FIG. 32 (g), the circle on the conical locus U having an angle θ returning to the X-axis line is rotated once, and one rotation is 2θ.
2 laps per minute.

At this time, the R circle surface is located in the middle of the X axis line and the S circle surface with the cross axis lines of the M and K axis lines orthogonal to each other, and is linked and linked with the X axis line and the S circle surface. , The rotation axis L of the circular surface is on the X axis when the K axis is orthogonal to the X axis as shown in FIG. 31A, and is Y when the M axis is orthogonal to the Y axis as shown in FIG. It is on the axis. In the end, the R circular surface makes a half rotation on the X-axis line by reversing and oscillating the angle θ by the horizontal direction, and reciprocates within the 2θ range by one rotation.
do. Further, the angle θ is an intersection angle formed on the acute angle side between the X and Y axis lines, and is also an open angle on the acute angle side between the rotation surface of the M axis line and the S circle surface due to the rotation of the X axis line.

Next, the secondary rotation which rotates in the opposite direction of the primary rotation Po with the X axis as the axis of rotation for the whole of each relationship with the R and S circles which make the primary rotation Po with the X axis as a reference. Ne is given simultaneously with the primary rotation Po. At that time, the forward / reverse rotation ratio is, for example, 1: 1 (1/1 to the numerator indicate a positive rotation primary rotation Po, and the denominator indicates a reverse rotation secondary rotation Ne).
If it is set to
The R-circle surface and the S-circle surface that perform The rotation angle position of the X axis to be set is set back in FIG. 32 (g) by 90 degrees, and is shown in FIG. 24 showing the forward and reverse rotations of the primary and secondary rotations Po and Ne.

That is, the primary rotation P with the X axis as the axis of rotation
The secondary rotation Ne for reversing o changes the phase of the S circle surface but does not rotate the S circle surface, and the forward / reverse rotation ratio is 1: 1 (1 /
The gap between the R circle surface and the S circle surface is changed from the minimum to the maximum or from the maximum to the minimum every half rotation (180 degrees) in 1). Therefore, in the case of only the primary rotation Po, the change in the gap between the R and S circular surfaces is 1 reciprocation of 1 increment / decrement per revolution of the X axis, while FIG.
As shown in the order of, when a secondary rotation Ne having a forward / reverse rotation ratio of 1: 1 (1/1) is added, the change in the gap between the R and S circles is increased by 1 and decreased by 1 for each half rotation of the X axis. Make a round trip. And further,
When the X-axis of FIG. 30 is rotated half a turn in the rotation direction, the gap between the R and S circular surfaces makes one reciprocation of 1 increase and 1 decrease, and the original FIG.
Return to 8.

That is, the change in the gap between the R and S circular surfaces in one rotation of the X-axis line to which the secondary rotation Ne of the forward / reverse rotation ratio of 1: 1 (1/1) is added is 2 reciprocations of 2 increase and 2 decrease. .. At that time, FIG. 3 showing the process of changing the gap between the R and S circular surfaces in the primary rotation Po.
1, 32 (a) to (o) are compared with FIGS. 18 to 29 showing the process of the gap change of the R and S circular surfaces in the combined rotation of the primary rotation Po and the secondary rotation Ne, and the reverse rotation is performed. The illustrated FIG. 30 corresponds again to FIG. 31A of the primary rotation Po.

In the operating principle 2 on this geometrical figure in the present invention, the change in the gap between the R-circle surface and the S-circle surface in this forward and reverse rotation is replaced by the stroke volume of the working chamber Fu, that is, the so-called air chamber volume change. Each of the air chambers A, B, C, D has its own stroke, and by increasing or decreasing the volume thereof, the rotary piston 30 and the skew plate 40 on the R and S circles intersecting on the piston intermediate shaft 33 on the K axis. It is intended to rotate the rotating main shaft 20 placed as an output shaft on the X-axis while rotating the rotating shaft. In this case, in the normal / reverse rotation, (positive) indicates the rotation of the rotary main shaft 20 that performs the primary rotation Po, the rotary piston 30, and the skew plate 40, and (reverse) indicates the phase plate 56 that performs the secondary rotation Ne (solved). The rotation of the means 4) or the phase housing 80 (solution means 8) is shown.

[0079]

BEST MODE FOR CARRYING OUT THE INVENTION The present invention belongs to either the above-mentioned operating principle 1 or the above-mentioned operating principle 2 on a geometrical figure in a geometrical structure and is classified into the above-mentioned solving means 1 to 8. Embodiments 1 to 8 that have structural differences and are based on the configurations of the respective solving means 1 to 8 (the solving means 1 is the form 1,
The solving means 2 has an embodiment of form 2, and the solving means 8 has an embodiment of form 8). In the classification of the embodiment, the Z-axis housing 70 as the inner shell in the housing 10 of the outer shell, or Although there is a structural difference whether or not the housing 60 or the phase housing 80 is incorporated, the form 1,
5 has the rolling shaft 72 and is common, and forms 2, 6
Both have the Z-axis 23 having the shaft plate 24, the Z-axis 23 has the shaft arm 25 in the forms 3 and 7, and the forms 4 and 8 are the rotary main shaft 20 having a straight shaft shape. Both operations are characterized by the same change.

Embodiments will be described below with reference to the drawings by various examples based on the above-mentioned relationships among geometric figures and the interrelated movements of the figures. It should be noted that, in FIGS.
Intake hole In through which the working medium flows in and out except 5, 36, 50
Illustration of the exhaust hole Ex, the igniter (or fuel injection valve) Ig, etc. is omitted, and in all the drawings for explaining the present invention, a sealing tool (piston ring in a reciprocating piston engine) such as a gas seal or an oil seal, Illustration of the cooling device, the cooling device, the lubricating device, etc. is omitted.

[0081]

First Embodiment First, in the first embodiment which belongs to the operation mode of the operating principle 1 on the geometrical figure based on the configuration of the solving means 1, the rotary piston 30 is formed into a circular plate to form a spherical surface. Four spaces A between R and S circles in G,
An embodiment shown in FIGS. 35 and 36 of the configuration by the common solving means 1 formed in B, C and D will be described.

In this embodiment, a spherical housing 1 is used.
If 0 is assumed to be divided into three parts, that is, a central part and both side parts thereof by two parallel cut planes aa and bb that sandwich the S circle surface at equal intervals as shown in FIG. 35, the central part becomes , The inner wall surface of an S-circular concentric circle that is larger than the S-circular surface is formed into a cylindrical shape with the groove bottom of the orbital gap 12, and both side portions leave an edge circumference of the concave inner wall 11 forming a spherical surface G and Y A substantially hemispherical body having the shaft plate chamber 15 in which the inner wall of the spherical surface G is cut out in a circular recess around the axis and the main bearing 13 of the bearing circular hole at the center of the side wall of the shaft plate chamber 15 on the Y axis. .

In the housing 10 constructed as described above, as shown in FIG. 35, the main bearings 13, 13 on both sides have shaft rod chambers 15 in which handle-like round rods are fixedly attached to the central portion of the outer surface by axial fixing. , 15 rotatably housed in the concave circular plate, the inner concave surface of which is a spherical surface G, and the axial plates 24 and 24, which are connected to each other on the X-axis by bridging and fixing each of the axial plates 24 and 24 to the intermediate oblique shaft. A Z-axis 23 having an overall Z-shaped integral structure is provided by the rod 26, both side shaft necks of the Z-axis 23 are formed in the journal portion, and the journal is fitted and rotatably supported. This Z-axis 23 connecting rod 26
At the center portion located at the ball center O, a shaft center 74 of a connecting element having a pin columnar shape that constitutes a pin joint joint 55 with the M axis as a connecting shaft, and rolling gears 76, 76 at both ends are provided. The rolling shaft 72, which is entirely tubular, is externally fitted with the X axis as the rotation axis.

On the R circle surface, both shaft plates 2 including the inner wall surface of the housing 10 forming a spherical surface G on each of the opposite sides sandwiching the S circle surface.
Rotating outer peripheral spherical arc surfaces 32, 32 rotatably contacting the inner concave surfaces of 4, 24, and the arcuate surfaces 31 on the front and back sides forming the arcuate contour planes of both spherical arc surfaces 32, 32 and having the K axis side as a chord. , 3
K, on two symmetrical arcuate plates with 1, 31, 31
A rotary piston 30 having a circular plate, in which a cylindrical piston intermediate shaft 33 is united, is arranged with the axis as a mounting axis.

The rotary piston 30 has a hinge pin receiver 5 consisting of a circular hole of a hinge joint 50 with the intersecting secant K on the sides of the piston intermediate shaft 33 on the side of the points Ka and Kb.
2, 52 are provided, and the piston shaft hole 34 having a flat hole-like hole that penetrates from the spherical arc surfaces 32, 32 on the X-axis along the R circle to the center of the piston intermediate shaft 33 is opened, and Rolling shaft 7 fitted onto connecting rod 26 in the middle of Z axis 23
2 is loosely inserted, and a piston pivot 35 of a pin receiving hole corresponding to the pin-shaped element of the shaft center 74 is provided at the center of the piston passage shaft hole 34 inside the piston intermediate shaft 33. When the shaft center 74 is pivotally attached to the piston center 35, the rotary piston 30 with the rolling shaft 72 on the X-axis as the base shaft (θ
The pin joint joint 55 that can swing in the angular range of x2) is composed.

Further, on the S-circle surface, the rotary pistons 3 are provided on opposite sides of the piston intermediate shaft 33 on the intersecting secant K, respectively.
0 front and back arcuate surfaces 41, 41, 41, 41 corresponding to the arcuate surfaces 31, 31, 31, 31 and the arcuate surface 41,
41, 41, 41 arcuate contour surfaces forming outer peripheral contours on the front and back sides,
Two arcuate plates having a symmetry smaller than a semicircle are formed from the chord side surfaces 42, 42 that slidably contact the shaft surface of the piston intermediate shaft 33, and the orbital gaps are formed on the arcuate contour surfaces of the arcuate plates. The slanted plate ring 4 which has an annular shape and is rotatably fitted to the plate 12.
A circular plate-like shape having a window penetrating into a rectangle consisting of four sides of upper and lower chord side surfaces 42, 42 facing each other on the K axis and inner peripheral surfaces of the oblique plate rings 43 on the left and right sides by connecting the inner peripheral surfaces of 3 to each other. The skew plate 40 is arranged.

On this slanting plate 40, a hinge joint 50 is provided for each of the hinge pin receivers 52, 52 of the rotary piston 30.
Hinge pins 51, 51 are formed so as to project inside the diagonal plate ring 43 located on the points Ka and Kb sides of the window frame, and the piston intermediate shaft 33 is mounted on the window frame that penetrates the K axis. When fitted along the pillar, the hinge pins and the hinge pin receivers 51, 52, 51, 52 which are given to each other are connected and fitted to form the hinge joint 50, and the oblique plate 40 and the rotary piston 30 intersect each other. The secant K is used as a base axis of the hinged connection so that the range (θ × 2) can be slidably connected.

Then, the oblique plates 40 on the S-circular surface close the respective inner concave surfaces forming the spherical surface G of the shaft plates 24, 24 including the inner wall surface of the housing 10 to form concave surfaces in the housing 10. To form two half-moon-shaped working chambers Ha and Ha, each of which is composed of a hemispherical constant-volume space, and the rotary piston 30 on the R-circular surface inversely proportions the volume of each half-moon-shaped working chamber Ha or Ha. It is formed in air chambers A, B, C and D that form two closed comb-shaped spaces that change.

In addition, each of the shaft plate chambers 15 and 15 is formed by engraving a fixed gear consisting of the internal gear of the fixed phase gears 14 and 14 on the X axis of each of the shaft plates 24 and 24. Is provided with gear pockets 28, 28 having a bag-like void having an opening on the side circumference, and both ends of the connecting rod 26 are fixed inside the gear pockets 28, 28. In addition, the rolling shaft 7
2 is a tube (hollow cylinder) -shaped shaft sleeve fixed to each of the opposite sides of the shaft center 74, and has a pitch circle diameter smaller than that of the fixed phase gears 14, 14 at the ends of both shaft sleeves. It is a straight shaft having a tube hole that penetrates on its own rotation axis by fixing the rolling gears 76, 76 formed of external gears,
When the connecting rod 26 of the Z-axis 23 is freely rotatably inserted into the tube hole and the rolling gears 76, 76 are housed in the gear pockets 28, 28 of the shaft plates 24, 24 in a free relation, the rolling gears 76, 76 Since only the tooth tops of the gears are exposed from the side circumferential openings of the gear pockets 28, 28, the fixed phase gear 1 which gives the exposed tooth tops of the rolling gears 76, 76 to each other.
The inscribed meshing is made possible so that it can be rolled over.

Then, when the rolling shaft 72 is rotated in the direction of the arrow, the rotary piston 30 connected to the rolling shaft 72 via the pin joint joint 55 makes a primary rotation Po on the conical locus U and at the same time the rolling gear 76. , 76 are inscribed in the pitch circle diameters of the fixed-phase gears 14 and 14 which are base circles, so that they rotate while rotating with the rolling shaft 72, while rotating in the opposite direction to the rotation, the shaft plate 24 of the Z-axis 23. , 24, the secondary rotation Ne along the conical locus J is performed. That is, the rolling shaft 7 interlocking with the rolling gears 76, 76.
The precession movement of 2 (conical movement) causes the secondary rotation Ne which is the reverse rotation of the rotary piston 30 on the cone locus J to change the phase of the rolling shaft 72 itself. The change in the phase of the rolling shaft 72 in the secondary rotation Ne acts so as to return the rotation axis L of the R circular surface from the X-axis line to the Y-axis line and then back to the X-axis line again per half rotation. As well as R,
The gap between the S circles is changed.

At that time, if the pitch circle diameter ratio between the fixed phase gear 14 and the rolling gear 76, which are given to each other, is 2: 1 as shown in FIG. 35, the rolling amount of the rolling gear 76 and the rolling amount in the opposite direction are calculated. Are equal to each other, the rolling axis 72 has the center O of the ball as the center of the turning, and the conical locus J with the Y axis as the axis of the turning is shown in FIGS. 16A to 16B and 16C. The secondary rotation Ne of the precession is performed in the opposite direction of the rotation in the order of FIGS. In other words, 90 degrees of rotation of the rolling shaft 72
As for the degree of rotation, the rotary piston 30 connected to the rolling shaft 72 via the shaft center 74 and the skew plate 40 are rotated by 90 degrees in the same direction, and the rolling shaft 72 itself rotates in reverse on the conical locus J. Direction is rotated by 90 degrees to change its own phase, and its forward and reverse rotations of 90 degrees each go through FIG. 16 (A) to (F) and then to FIG. 17 (G). 6
As shown in the order of FIG. 7), the forward / reverse rotation ratio is 1: 1 (1 /
1) is established and the gap difference between the rotary piston 30 and the skew plate 40 is changed from the minimum to the maximum or from the maximum to the minimum.

From there, when the rolling shaft 72 is further orbitally rotated in the forward / reverse direction for 90 degrees, it goes from (G) to (H) to (K) in FIG. 8 through 12 to FIG. 13), the rotary piston 3
0, the air chambers A, B, C, D formed between the skew plate 40
The volume of the air chamber of the subject changes again within the maximum range. When the rolling shaft 72 is further given a rotation (half rotation) corresponding to 90 ° + 90 °, a rotation (half rotation) of the opposite rotation of 90 ° + 90 ° is also given to each air chamber A, B. , C, D are subjected to the same maximum range of volume change twice as described above, and the process returns to FIG. 16A (the geometrical figure is FIG. 1) which is the starting point.

After all, one rotation of the rolling shaft 72 whose forward / reverse rotation ratio is set to 1: 1 (1/1) corresponds to one revolution of the rolling shaft 72 which makes the Z-axis 23 rotate in the opposite direction one revolution. And the rotary piston 30 is 2 with respect to the skew plate 40 in the meantime.
By reciprocating swinging, each of the air chambers A, B, C, D makes four changes in volume corresponding to four strokes. The air chamber space A,
In the four changes of B, C and D, the working medium is sucked in the transition from the minimum volume to the maximum volume, the working medium is compressed in the reduction process from the maximum volume, and ignition or fuel is injected just before the end. The working medium is burned, the working medium expands at the next expansion of the air chamber gap, and the waste air is discharged at the next contraction.

In this embodiment, each of the four air chambers A, B, C, and D has its normal / reverse rotation angle (working angle) between the rolling axis 72 on the X axis and the Z axis 23 on the Y axis. 90 air chamber volume
The air chamber volume is increased / decreased twice per revolution of the shaft by changing each time. If the intake stroke, compression stroke, expansion stroke and exhaust stroke stroke work are applied to the four changes in the air chamber volume per one rotation of the shaft to operate, the rotary piston engine of the present embodiment is a four stroke cycle reciprocating piston engine (4 cylinders x 2) It corresponds to an engine, but for that purpose, it faces the air chambers A, B, C, D as appropriate.
An intake hole In and an exhaust hole Ex for letting the working medium flow in and out are provided, and the ignition chamber Ig is examined by inspecting the combustion chamber portion. In the mode of a diesel engine, a fuel injection valve (hereinafter, the fuel injection valve is included in the ignition device Ig). Insert only the igniter Ig).

The working medium inflow / outflow holes In and Ex are the arcuate surfaces 4 of the oblique plate 40 facing the air chambers A, B, C and D, respectively.
Oblique plate flow passage holes 49, 49, 4 which communicate with and open to the outer peripheral surface of the oblique plate ring 43 from each of 1, 41, 41, 41 separately.
9 and 49, and two streak housing flow passage holes 19 and 19 each formed of a groove-shaped hole that penetrates from the inner wall surface of the housing 10 on the rotation circumference of the hole of the outer peripheral surface to the outer wall of the housing 10. Further, the igniter Ig includes the left and right half-moon shaped operation chambers Ha,
Two pieces of each Ha are inserted into the wall of the housing 10 at positions facing the perforated portions of the housing flow passage holes 19 and 19,
Alternatively, although not shown, one may be provided in each half-moon-shaped working chamber Ha by inserting the two in an intermediate position.

The oblique plate flow passage holes 49, 49, 49, 49
Each share the intake hole In and the exhaust hole Ex,
Each of the outer peripheral surface hole openings is opened on the same rotation circumference at regular intervals of 90 degrees at the central angle of the skew plate 40, and the two housing flow passage holes 19, 19 are formed in the housing 10. Intake holes In are provided on the leading side of the two lines with respect to the rotation direction of the oblique plate 40, with the line lengths being approximately 1/4 of the circumference of the wall surface and being continuously formed in the same circle. The exhaust side Ex is on the delayed side. Also, four oblique plate flow path holes 4
9, 49, 49 and 49 are housing flow passage holes 19 and 19
Since it is rotating on the opening circumference of the inner side hole mouth, when the connection is synchronized with the increase or decrease of the air chamber space of each air chamber A, B, C, D, the air chambers A, B In C and D, either intake or exhaust holes In or Ex are opened to perform either intake or exhaust stroke, and if connection is over, either compression or expansion stroke is performed, but operation by ignition tool Ig Media ignition is synchronized at the peak of compression work.

That is, as the air chambers A, B, C, and D are sequentially rotated once every 90 degrees, the housing passage hole 1 of the preceding intake hole In is advanced for the first 90 degrees.
9, the intake stroke is performed, and in the next 90 degrees, the working medium is ignited by being disconnected from the connection with the intake hole In and the compression stroke, and the expansion stroke is performed in the next 90 degrees closed. Since the remaining 90 degrees is connected to the housing flow path hole 19 of the exhaust hole Ex and the exhaust stroke is performed, the air chamber A,
Each of B, C, and D performs one stroke every 90 degrees of progress, and each progresses a stroke other than the same stroke that does not conflict with each other at the position of the same rotation angle.

From the connection of the above operations, in the four air chambers A, B, C and D shown in FIG. 35, the air chamber A ends the exhaust stroke and starts the intake stroke, and the air chamber B ends the expansion stroke. The exhaust stroke is started, the air chamber C is in the expansion stroke, and the air chamber D is in the rotation angle position where the compression stroke is started. That is, FIG. 3 showing an example of this mode 1
In Fig. 5, the expansion pressure in the next air chamber C instead of the air chamber B that has completed the expansion stroke spreads the gap between the rotary piston 30 and the skew plate 40, and the primary rotation that is the direction of force to the rotary piston 30 is performed. Secondary rotation N on the Z-axis 23 while making Po
The Z-axis 23, which is caused to e and makes its secondary rotation Ne, is used as the output shaft in the internal combustion piston engine.

[0099]

Embodiment 2 of Embodiment 2 In the configuration of the embodiment of Embodiment 1 described above, the rolling shaft 72 mounted on the connecting rod 26 of the Z-axis 23.
Is replaced with a pivot 88 of a circular element, the rotary piston 3
It is possible to reversely rotate the Z axis 23 with respect to 0 and the skew plate 40. Next, an embodiment of the form 2 shown in FIG. 39 according to the structure of the solving means 2 and the operating principle 1 on the geometrical figure will be described. This embodiment is based on the common solving means 1 in which the rotary piston 30 is formed into a circular plate and the R and S circles in the spherical surface G are formed into four spaces A, B, C and D. Is.

In the embodiment of the second embodiment, the pivot connector 88 of the circular body element forming the pin joint joint 55 has a hole vertically penetrating the side surface thereof, and the connecting rod 2 of the Z axis 23 is formed.
6 is inserted, but the Z-axis 23 has a spherical bar G on each of the inner side surfaces facing each other by fixing a handle-shaped round bar to the center of the outer side surface.
Forming a Z-shaped integral structure from the shaft plates 24, 24, which are biconcave circular plates arranged side by side, and the connecting rod 26 on the X axis that bridges each of the shaft plates 24, 24 to the intermediate oblique axis. X is attached to the center of the connecting rod 26 located at the ball center O.
The pivot 88 is externally fitted with the axis as a mounting axis, and the pivot 88 is connected and fitted to the piston pivot 35 having a circular hole provided at the inner center of the rotary piston 30.

Further, the shaft plate chambers 15 and 15 are formed by notching each of the opposing inner walls forming the spherical surface G of the housing 10 through which the Y axis passes through into circular recesses, and the through holes in the side wall center portions of both shaft plate chambers 15 and 15. The main bearings 13 and 13 are provided, the shaft plates 24 and 24 are rotatably accommodated in the shaft plate chambers 15 and 15, and the two shaft necks of the Z shaft 23 are fitted into the main bearings 13 and 13. Let the bearing. The Z-axis gear 27, which is an external bevel gear, is attached to one shaft neck of the Z-axis 23, and the edge circle of the skew plate ring 43 is also attached to the skew plate 40 at the same pitch circle as the Z-axis gear 27. Bevel plate ring gear 44 formed by engraving on an externally toothed bevel gear having a diameter
And an intermediate meshing gear 5 having an intermediate mesh between the Z-axis gear 27 and the skew plate ring gear 44, which rotate in opposite directions.
When 4 is interposed and meshed with them, and the Z-axis 23 is rotated in the direction of the arrow, the skewed plate ring gear 44 rotates in the opposite direction of the Z-axis gear 27 via the intermediate gear 54.

The rotation of the skew plate ring gear 44 causes the skew plate 4 to rotate.
At the same time that the rotary piston 30 connected to 0 makes a primary rotation Po on the connecting rod 26, the connecting rod 26 makes a secondary rotation Ne on the conical locus J in the rotation direction of the Z axis 23. Secondary rotation N rotating in the opposite direction of the primary rotation Po
e is the rotation axis L of the R circle per half rotation from the X-axis to Y
It acts so as to return to the axial line and then to the X-axis line again, and changes the gap between the R and S circular surfaces in the same manner as the primary rotation Po. At that time, the Z-axis gear 27 and the oblique plate ring gear 44
If the ratio of the pitch circle diameters is equal to, for example, 1: 1 as shown in FIG. Since the gap between the rotary piston 30 and the skew plate 40 shows the maximum change when moving the same distance in the direction and rotating by 90 degrees in the forward and reverse directions, the following operation and working medium inflow / outflow mechanism have the above-described modes. This is exactly the same as the case in the above embodiment.

[0103]

[Embodiment 3 of Embodiment 3] An embodiment of Embodiment 3 is shown in FIGS.
As shown in FIG. 5, the shaft plates 24, 24 of the Z-axis 23 in the embodiment of the above-described mode 2 are replaced by shaft arms 25, 2 of arm bars of arbitrary shapes.
5 and is operated based on the solving means 3, which belongs to the operating principle 1 on the geometrical figure as in the case of the embodiment of the above-mentioned mode 2, and the rotary piston 30.
Is based on the common solving means 1 in which a circular plate is formed and the R and S circular surfaces in the spherical surface G are formed into four spaces A, B, C and D.

The Z-axis 23 in this embodiment is the double shaft plate 2
In contrast to the embodiment of the above-described embodiment 2 in which 4 and 24 are arranged side by side on the outer side of the spherical surface G, each of the plate-shaped or rod-shaped shaft arms 25, 25 arranged immediately inside the spherical surface G forms a middle rod. The connecting rod 26 is integrally connected and fixed, but the pivot connector 88 is rotatably fitted onto the central portion of the connecting rod 26 located at the ball center O similarly to the configuration in the embodiment of the second embodiment. . The Z-axis 2 is attached to the wall of the housing 10 of this embodiment.
The main bearings 13, 13 for supporting the shaft 3 are provided through the shaft plate chamber 1
There is no formation of Nos. 5 and 15, and both side walls of the orbital gap 12 are spherical surfaces G
Concave inner walls 11, 11 of the housing 10 facing each other
Is.

Therefore, each of the air chambers A, B, C and D has an arcuate surface 31 of the rotary piston 30 including the concave inner wall 11 of the housing 10 and the shaft surface of the piston intermediate shaft 33, and the oblique plate 40. , 41, and is a sealed space. In this case, each of the shaft arms 25, 25 is accommodated together with the connecting rod 26 in the piston through hole 34 in a free relation. Also in this embodiment, the Z-axis gear 27 is provided to the Z-axis 23-axis neck, the oblique plate ring gear 44 is provided to the oblique plate 40, and the intermediate gear 54 that meshes with them is interposed. The operation according to the above is the same as in the case of the embodiment of the second aspect, and the working medium inflow / outflow mechanism is exactly the same as in the case of the embodiments of the first and second aspects.

[0106]

[Embodiment 4] Next, based on the configuration of the solving means 4 and the common solving means 1, the operating principle 2 on the geometrical figure.
An example of the fourth form of the operation form belonging to the above will be described. In this embodiment, the rotary spindle 20 having a straight axis is attached to the Z axis 23 which is the curved axis in the above embodiment, and instead of the shaft plates 24 and 24 of the Z axis 23 or the shaft arms 25 and 25. The phase plates 56, 56, which are concave circular plates having the X axis as the axis of rotation, are attached about the Y axis, but the rotary piston 30 and the skew plate 40, which are circular plates attached on the R and S circle planes, are the same as those described above. The configuration is the same as in the example.

In this embodiment shown in FIGS. 49 and 50, the inner wall surface of the housing 10 having a spherical outer shape is spherical surface G.
A main bearing 1 formed of a spherical surface larger than the concentric spherical surface G and having circular holes in both opposing walls of the housing 10 through which the X axis passes.
3 and 13 are provided, and both shaft necks of the rotary main shaft 20 are fitted and supported on the main bearings 13 and 13, respectively. The rotating spindle 2
A circular shaft center 21 having a pin receiving hole is provided in the central portion located at the ball center O of 0, and the rotary main shaft 20 is inserted into the piston through shaft hole 34 of the rotary piston 30 and the pin of the piston center 35 is inserted. When the shaft center 21 is pivotally attached to the element, the rotary piston 30 can swing in the range of (θ × 2) angle with the M axis as the central axis of the connection and the rotary spindle 20 on the X axis as the base axis. The pin joint joint 55 is constructed.

Further, on each of both sides of the slanting plate ring 43, a concave circular plate whose inner surface is a spherical surface G is rotatably slidably in contact with the side surface circumference of the slanting plate ring 43 and the spherical inner wall of the housing 10. The phase plates 56, 56 are fitted to each other, and both phase plates 5
Circular holes of the phase plate bearings 57, 57 are provided on the points P, P of 6, 56 to insert the rotary spindle 20 therein. Then, the skew plate 40 on the S-circular surface is the phase plate 5 including the inner peripheral surface of the skew plate ring 43.
The inner concave surfaces of the spherical surfaces G of 6,56 are closed to form two half-moon-shaped working chambers Ha, Ha in the housing 10 which are hemispherical constant volume spaces facing each other. Furthermore,
Each of the half-moon-shaped working chambers Ha, Ha is formed by an air chamber A, B, C, D in which a rotary piston 30 on the R circular surface forms two closed comb-shaped spaces that change volume inversely proportionally. To do.

In this embodiment, a phase plate gear 58 of an external bevel gear is provided on the outer surface of the phase plate 56 with the phase plate bearing 5.
7, the main shaft gear 22 of the external bevel gear having the same pitch circle diameter as that of the phase plate gear 58 is provided in parallel with the shaft neck of the rotary main shaft 20 outside the phase plate gear 58. When the rotating main shaft 20 is rotated in the direction of the arrow after interposing an intermediate meshing intermediate gear 54 that meshes with both the gears 58 and 22 to rotate them in opposite directions, the pin joint is attached to the rotating main shaft 20. At the same time as the rotary piston 30 connected via the joint 55 makes a primary rotation Po on the conical locus U, the phase plate gear 58 rotates in the opposite direction of the main shaft gear 22 via the intermediate gear 54.

That is, the phase plate 5 interlocked with the phase plate gear 58.
6 makes a secondary rotation Ne, which is the reverse rotation of the rotation main shaft 20, on the conical locus J to change the phase of the skew plate 40. The phase change of the skew plate 40 in the secondary rotation Ne is half. With respect to the rotation, the rotation axis L of the R circle surface is changed from the X-axis line to the Y-axis line,
Then, it works so as to return to the X-axis again, and the primary rotation P
As with o, the gap between the R and S circles is changed. At that time,
When the pitch circle diameters of the main shaft gear 22 and the phase plate gear 58, which are given to each other, have the same ratio of 1: 1 as shown in FIG. 49, the rotary main shaft 20 and the phase plate 56 have the same rotation ratio. And move the same distance in opposite directions, and
The gap between the rotary piston 30 and the skew plate 40 shows the maximum change in the rotation of a degree.

That is, 90 degrees of rotation given to the rotary main shaft 20.
As for the degree of rotation, the rotary piston 30 and the skew plate 40, which are connected to the rotary main shaft 20 via the shaft center 21, are rotated by 90 degrees in the same direction, and the phase plates 56, 56 are conical loci in the opposite direction. Rotate 90 degrees on J to change the phase of the skew plate 40, and the rotation of the forward and reverse directions by 90 degrees is performed through FIGS. 33 (A) to (F) to FIG. 34 (G). As shown in FIG. 24 through FIGS. 18 to 23, the forward / reverse rotation ratio is 1: 1.
By establishing (1/1), the rotary piston 30 and the skew plate 40
The gap difference between and is changed from the minimum to the maximum, or from the maximum to the minimum. From there, rotate 90 degrees to rotate the spindle 20.
, The air chamber spaces A, B, C and D, which are the gaps between the rotary piston 30 and the skew plate 40, are shown in FIGS. 34 (G) to (H).
Through (K) through (L) (in the case of the geometrical figure, FIG. 24 through FIG. 25 through FIG. 29 through FIG. 30), the maximum range is changed again.

Then, when a half-rotation equivalent to 90 ° + 90 ° is further applied to the rotary main shaft 20, each air chamber A, B,
FIG. 33 (A), which was started after performing the same maximum range of volume change twice for C and D (FIG. 18 for geometrical figures).
Return to. That is, one rotation of the rotary spindle 20 in which the forward / reverse rotation ratio is set to 1: 1 (1/1) causes the respective phase plates 56 to move through the rotary spindle 2.
One rotation is made in the opposite direction of 0, and one rotation of the phase plate 56 causes the rotary piston 30 to make two reciprocating movements with respect to the skew plate 40, so that each air chamber A, B, C, D has four strokes. 4 changes in volume corresponding to

In the present embodiment, each of the air chambers A, B, C and D has a phase plate 5 mounted on the rotating main shaft 20 on the X axis and on the Y axis.
At a rotation angle (working angle) opposite to that of 6, the air chamber volume is changed at every 90 ° rotation, and the air chamber volume is reciprocated twice for one rotation of the shaft. After all, if the stroke work of intake, compression, expansion, and exhaust is applied to the four changes of the air chamber volume per one rotation of the shaft to operate, the rotary piston engine of the present embodiment is a four stroke cycle reciprocating piston engine (4 Cylinder x 2) Equivalent to an engine. Therefore, a suction hole In and a discharge hole E for letting the working medium flow in and out facing the air chambers A, B, C, D.
x is provided, and a portion of the combustion chamber is checked to insert the ignition tool Ig.

The intake / exhaust holes In, Ex are opened, for example, from the arcuate surfaces 41 of the skew plate 40 facing the air chambers A, B, C, D to the outer peripheral surface of the skew plate ring 43. The oblique plate passage holes 49, 49, 49, 49 and the grooved holes penetrating from the inner wall surface of the housing 10 to the outer wall of the housing 10 on the rotation circumference of the hole opening on the outer peripheral surface are crossed to form one set. Two sets of housing flow passage holes 19 and 19 are provided. Further, the igniter Ig is provided for each of the left and right half-moon-shaped working chambers Ha, Ha, and each housing flow passage hole 1 for checking the outer peripheral surface hole of each oblique plate flow passage hole 49.
At least one piece is inserted into the wall of the housing 10 at a position opposite to 9.

The oblique plate flow passage holes 49, 49, 49, 49
Each share the intake hole In and the exhaust hole Ex,
Each of the outer peripheral surface hole openings is opened on the same rotation circumference at equal intervals of 90 degrees at the central angle of the oblique plate 40.
In addition, the two sets of housing flow passage holes 19, 19 each have a length of about ¼ of the circumference of the inner wall surface of the housing 10 along the opening rotation circumference of each oblique plate flow passage hole 49. The two lines having the line length are crossed, and two sets are continuously opened within the circumference length of 1/2 of the inner wall surface circumference of the housing 10.
In the set, the leading side in the rotation direction of the skew plate 40 is the intake hole In, and the trailing side is the exhaust hole Ex.

In this embodiment configured as described above, the air chamber volume of each air chamber A, B, C, D is increased or decreased by 90 degrees of rotation given to the rotary main shaft 20 as described above. Each skewed plate flow passage hole 49 has a housing flow passage hole 1
Since it rotates on the opening circumference of the inner side hole mouths of 9 and 19, the connection accompanying the rotation is synchronized with the volume increase / decrease of the air chambers A, B, C and D, and at the time of igniting the working medium by the igniter Ig. When synchronized with the highest compression stroke, each air chamber A,
In the progress of each rotation of 90 degrees during one rotation of B, C, and D, the intake hole In that precedes the first rotation of 90 degrees
Is connected to the housing flow path hole 19 to perform an intake stroke, and in the next 90 °, the working stroke at the end of compression is ignited by deviating from the connection with the intake hole In, and further The expansion stroke is performed by the rotation of 90 degrees, and the exhaust stroke is performed by being connected to the housing flow path hole 19 of the exhaust hole Ex in the remaining rotation of 90 degrees. At that time, the air chambers A, B, and
When C and D have the same rotation angle position, the strokes other than the same are advanced.

From the connection of the above operations, in the four air chambers A, B, C and D shown in FIG. 49, the air chamber A ends the exhaust stroke and starts the intake stroke, and the air chamber B ends the expansion stroke. The exhaust stroke is started, the air chamber C is in the expansion stroke, and the air chamber D is in the rotation angle position of the compression stroke start. In FIG. 49, the expansion pressure of the air chamber C instead of the air chamber B is the rotary piston 30 and skew plate 4
The rotational main shaft of the output shaft is expanded by widening the gap between the rotational piston 30 and the primary rotation Po, which is the direction of the force, while the phase plate 56 is rotated by the secondary rotation Ne to change the phase of the skew plate 40. It is intended to rotate 20.

[0118]

[Embodiment of Form 5] The embodiment of form 5 is based on the solving means 5 and the common solving means 1,
Shaft plates 24, 24 of the Z-axis 23 in the embodiment of the above-mentioned mode 1
In place of the above, since the Z-axis housing 70 of a spherical shell having a spherical space is incorporated in the housing 10 in a rotatable fitting state, it belongs to the operating form of the operating principle 1 on the geometrical diagram, The operation is performed by connecting the Z-axis 23 and the shaft plates 24, 24 to the Z-axis housing 7.
If replaced with 0, it is similar to the case of the embodiment of the first embodiment, but the air chambers A, B, C, D in this embodiment are formed in the Z-axis housing 70.

That is, in this embodiment shown in FIG.
The inner wall surface of the housing 10 having a spherical outer shape is formed as a rotation surface concentric with the Y axis larger than the spherical surface G, and main bearings 13 are provided on both opposing walls of the housing 10 through which the Y axis passes. In the housing 10 thus formed, the housing shaft 7 made of a handle-shaped round bar is provided on each of the opposing outer surfaces on the Y-axis.
Incorporating the spherical Z-axis housing 70 having an inner side surface formed into a spherical surface G enclosing the R and S circular surfaces by fixing 1 to the shaft, and fitting the housing shafts 71 and 71 into the main bearings 13 and 13. When inserted and supported by the shaft, the Z-axis housing 70 is freely rotatably fitted in the inner wall surface of the housing 10 with the Y-axis as the rotation axis.

On the Z-axis housing 70, an orbital gap 87 of a groove that circulates on the inner surface along the extension plane of the S-circle is cut, and the oblique plate ring 43 is rotatably fitted in the orbital gap 87. And the slanting plate 40 is constrained, and rolling bearings 73, 73 are provided on opposite sides through which the X axis penetrates to form a straight shaft-shaped rolling shaft 72.
Bearing the bilateral shaft neck journals. Since the connecting rod 26 is not mounted on the X-axis line in the Z-axis housing 70,
The rolling shaft 72 does not necessarily need a tube hole penetrating on its own axis, but the central portion of the rolling shaft 72 located at the ball center O is provided with a pin receiving hole with the M axis as a drilling axis. Is a central part 74 of a circular body, and the central part 74 is pivotally attached to a piston center 35 composed of a pin column mounted inside the rotary piston 30 to form a pin joint joint 55.

Further, the housing 10 having the S circle surface as the center
Fixed phase gears 14, 14 of an internal gear having a pitch diameter larger than a circumference whose radius is the opening angle of the X and Y axes are fixed to each of the opposing inner walls with the Y axis as the center. Rolling gears 76, 76 of external gears having a pitch circle diameter smaller than that of the phase gears 14, 14 are fixed to both ends of the rolling shaft 72 so that they can roll on the fixed phase gears 14, 14 provided respectively. When the rolling shaft 72 is brought into contact with each other and is rotated in the direction of the arrow, the rotary piston 30 connected to the rolling shaft 72 via the pin joint joint 55 is the same as in the case of the embodiment 1 described above. At the same time as performing the primary rotation Po on the conical locus U, the rolling gear 7
Since the pitch circle diameter of 6 rotates inscribed in the pitch circle diameter of the fixed phase gear 14 serving as the base circle, the secondary circle rotates along the conical locus J in the opposite direction of the rotation while rotating with the rolling shaft 72. Ne.

Further, as shown in FIG. 53, the connection between the rotary piston 30 and the skew plate 40 and the volume change of the air chambers A, B, C and D caused by the above-mentioned operation are as shown in FIG. If the pitch circle diameter ratio is set to 2: 1, it is the same as the case of the embodiment of the above-mentioned form 1. In / out holes for working medium In, Ex
In the above, although not shown in the drawing, in the Z-axis housing 70 facing each of the half-moon shaped operation chambers Ha, Ha, two pairs of housing flow passage holes 89, 89, 89, 8 penetrating the Z-axis housing 70 wall
Drill 9 The two housing flow passage holes 89, 89 facing the same half-moon-shaped working chamber Ha have one of the intake holes In and the other of the exhaust holes E on the rotation circumferential surfaces other than the same with the Y axis as the rotation axis.
x are drilled at positions substantially opposite to each other, and each of the two crescent-shaped working chambers Ha, two housing flow passage holes 89 facing Ha.
89, 89, and 89 are drilled on the same plane with the R circular surface when the X and Y axis lines are orthogonal to the K axis line as a reference.

The housing flow path hole 8 is also provided in the housing 10.
Housing flow consisting of grooved holes each having a circumference length of about 1/2 of the circumference of the inner wall surface from the inner wall surface to the outer wall on the four opening rotation circles in which 9, 89, 89, 89 are opened. The passage holes 19, 19, 19, 19 are made to communicate with each other so as to be connected to the respective casing passage holes 89 provided on the same circumference of rotation. At that time, the two streak-shaped housing flow passage holes 19 and 19 that open toward the same half-moon-shaped working chamber Ha are bored in the same rotation angle of the housing 10 by half the circumference length of each other. The lag side of the two lines in the rotation direction of the Z-axis housing 70 is the intake hole In, and the lead side is the exhaust hole Ex.
The two lines that open toward a and Ha are drilled in the same rotation angle and arranged in parallel.

Although not shown, the igniter Ig has an ignition hole (a fuel injection hole in the case of a diesel engine) 86 of an ignition port that penetrates the Z-axis housing 70 wall regardless of which half-moon shaped operation chamber Ha is faced. At an intermediate position between the two housing flow passage holes 89, 89, on a rotation circumference different from the opening rotation circumference of the housing flow passage holes 89, 89, and in both half-moon-shaped working chambers Ha, Ha. They are provided so as to face each other, on which the respective ignition holes 8 are provided.
At least two pieces are inserted into the wall of the housing 10 on the circumference of rotation for checking 6 and separated from each other by the central angle of the housing 10 at right angles. Alternatively, the igniter Ig can be attached freely by, for example, inserting the required number of the Z-axis housing 70 or the slanting plate 40 in an embedded manner, but in that case, the ignition hole 86 is not necessary.

In this embodiment constructed as described above, Z
90 degrees of rotation of the shaft housing 70 and the rolling shaft 72 changes the air chamber volume of each air chamber A, B, C, D from the minimum to the maximum or from the maximum to the minimum, and synchronizes with the volume change. The working medium inflow / outflow holes In and Ex are closed or opened as appropriate. That is, as the Z-axis housing 70 rotates, each housing flow path hole 8
When 9 is connected to the housing flow passage hole 19 provided thereto, intake is performed in any of the air chambers A, B, C, D corresponding to the connection space, and intake or exhaust is performed by opening any of the exhaust holes In, Ex. Either stroke is performed, and if connection is over, either stroke of compression or expansion is performed. It should be noted that the ignition of the working medium by the igniter Ig is synchronized with the maximum compression stroke of each of the air chambers A, B, C, D.

From the connection of the above construction and operation, in the four air chambers A, B, C and D shown in FIG. 53, the air chamber A ends the exhaust stroke and the intake stroke, and the air chamber B ends the expansion stroke. The exhaust stroke, the air chamber C is in the expansion stroke, and the air chamber D is in the rotation angle position where both start the compression stroke.
Instead, the expansion pressure of the air chamber C widens the gap between the rotary piston 30 and the skew plate 40 to cause the rotary piston 30 to perform the primary rotation Po, which is the direction of the force, and to change the phase of the rolling shaft 72. The Z-axis housing 7 also as the secondary rotation Ne of
It is intended to rotate the housing shaft 71, which is attached to 0.

[0127]

[Embodiment 6] Based on the configurations of the solving means 6 and the common solving means 1, the operating principle 1 on the geometrical figure
In this embodiment belonging to the above-mentioned embodiment, instead of the ring-shaped skew plate ring 43 attached as the outer periphery of the skew plate 40 in the embodiment of the above-mentioned mode 2, a spherical casing 60 having an inner hollow surface having a spherical surface G is formed. Is incorporated in the housing 10.

That is, in this embodiment shown in FIG. 56, the inner wall surface of the housing 10 is formed on the Y-axis by forming a spherical surface concentric with the spherical surface G larger than the spherical surface G or a rotating surface concentric with the Y-axis larger than the spherical surface G. Main bearings 13, 1 on the opposite wall of the housing 10
The housing 6 is formed into a spherical inner shell having an inner side surface forming a spherical surface G by enclosing R and S circular surfaces.
0 is assembled in the housing 10 so as to be rotatable and slidable with the Y axis as the axis of rotation. The housing 60 has a partition plate-shaped housing slanting plate 61 made of two symmetrically-arranged arcuate plates that are fixed to the S-circular surface of the housing 60 and separate the internal space of the housing 60 from both sides, and both of them are opposed to each other on the Y-axis. Shaft plate chambers 64, 64 with inner walls cut out in circular recesses
And the housing bearing 6 of a circular hole penetrating through the center of the wall of each shaft plate chamber 64.
3 and 3.

The Z-axis 23 is rotatably supported by the housing bearings 63, 63 and the main bearings 13, 13 on both sides of the Z-axis so that both shaft necks are fitted and the Z-axis 23 is rotatably supported. Similar to the configuration of the embodiment, a handle-shaped round bar serving as a shaft neck is fixed to the central portion of the outer surface and is rotatably housed in the shaft plate chambers 64, 64. The shaft plates 24, 24 of the plate and the connecting rod 26 on the X axis for connecting the shaft plates 24, 24 to the intermediate oblique shaft are connected to each other to form a Z-shaped integral structure. The central part of the connecting rod 26 of the Z axis 23 also has a pivot member 8 of a circular body element.
8 is attached and pivotally attached to a piston pivot 35 having a circular hole formed in the center of the rotary piston 30.

Further, in the skewed board 61, the two chord side surfaces 42 and 42 facing each other on the K-axis by the two arcuate boards smaller than a semicircle having their arcuate contour surfaces fixed to the inner surface of the housing 60.
And the inner surface of the housing 60 located on the side of the points Ka and Kb is formed in a partition plate shape inside the housing 60 having a rectangular window having four sides, and the point Ka of the window frame, The hinge pins 51, 51 of the pin pillar are provided on the side of the point Kb, the piston intermediate shaft 33 is inserted into the window frame, and the hinge pin receiver 52 of the rotary piston 30 is provided to each of the hinge pins 51, 51. , 52 are fitted to each other to form the hinge joint 50, the housing skew plate 61 on the S circle surface and the rotating piston 30 on the R circle surface use the intersecting secant K as the base axis of the hinged connection (θ × 2 ) Is slidably connected, and four air chambers A, B, C, which form a comb-shaped space sealed in the housing 60, are formed.
Form D.

The housing 60 is provided with the housing gears 62, 62 of external bevel gears having a pitch circle diameter larger than the hole diameters of the housing bearings 63, 63 on both outer surfaces facing each other around the housing bearing 63 holes. The Z-axis gear 27 of the external bevel gear having the same pitch circle diameter as that of each of the housing gears 62 is also provided on both shaft necks of the Z-axis 23 located outside of each of the housing gears 62, and the Z-axis gears 27 are provided together. When the intermediate gear 54 having an intermediate mesh is interposed between the gear 62 and the Z-axis gear 27 so as to mesh with them, and the Z-axis 23 is rotated in the direction of the arrow, the intermediate gear 5
Each of the housing gears 62 rotates in the opposite direction of the Z-axis gear 27 via 4.

The rotation of the housing gear 62 causes the rotary piston 30 connected inside the housing 60 to make a primary rotation Po on the conical locus U on the connecting rod 26, and at the same time, to rotate the connecting rod 26 in the rotating direction of the Z axis 23. Causes a secondary rotation Ne on the conical locus J. The secondary rotation Ne, which is the reverse rotation of the primary rotation Po, works so as to return the rotation axis L of the R-circle surface from the X-axis line to the Y-axis line and back to the X-axis line again per half rotation. Similarly, since the gap between the R and S circle surfaces is changed, if the pitch circle diameters of the Z-axis gear 27 and the housing gear 62, which are given to each other, are made to operate at the same ratio of 1: 1, they are moved in opposite directions. Move a distance equal to
The rotary piston 30 and the diagonal plate 6 of the housing during the rotation of 0 degree
The gap with 1 changes the maximum.

The respective volumetric changes of the air chambers A, B, C and D created by the gap change between the rotary piston 30 and the casing skew plate 61 and the 4-stroke operation are the same as in the case of the embodiment of the second embodiment. Also, in the working medium inflow / outflow holes In and Ex, although not shown, from the inner side surface of the housing 60 facing the air chambers A, B, C, and D, or each plate surface 41 of the housing skew plate 61. Housing flow passage holes 69, 69, 69, 69 communicating with the outer surface of the housing 60
And two streak housing flow passage holes 19 and 19 penetrating the wall of the housing 10 on the outer circumference of the hole on the outer side surface thereof, and the igniter Ig also faces the perforated portions of the housing flow passage holes 19 and 19. The left and right half-moon-shaped working chambers H are formed on the wall of the housing 10 on the circumference of rotation, which covers the outer surface hole opening of each housing flow path 69.
Insert at least one each for a and Ha. After all, each casing flow passage hole 69 in this embodiment is a substitute for the oblique plate flow passage hole 49 in the embodiment of the above-described mode 2, and the mounting and operation of both the housing flow passage hole 19 and the ignition tool Ig are as described above. This is exactly the same as the case of the embodiment of form 2.

[0134]

[Embodiment 7] The embodiment 7 of the embodiment 7 has a configuration based on the solving means 7 and the common solving means 1,
In place of the ring-shaped skew plate ring 43 attached as the outer circumference of the skew plate 40 in the embodiment of the above-described mode 3, a spherical housing 60 having a hollow inside is incorporated in the housing 10. At the same time, the Z-axis 23 in the embodiment of the above-mentioned mode 6
Each of the shaft plates 24, 24 is replaced with a shaft arm 25, 25 having an arbitrary shape to operate, and belongs to the above-mentioned operating principle 1 on the geometrical figure.

That is, in this embodiment shown in FIG.
The spherical surface G is concentric with the spherical surface G or the spherical surface G is concentric with the Y-axis, as in the configuration of the embodiment of the sixth aspect.
It is formed on the inner wall surface of the larger housing 10, and Y
Main bearings 13 and 13 are provided on both axially opposite walls of the housing 10 to form a spherical inner shell having an inner surface forming a spherical surface G by enclosing the R and S circular surfaces in the housing 10. The housing 60 is assembled so as to be rotatable and slidable with the Y axis as the rotation axis. The housing 60 does not have the shaft plate chambers 64, 64 in the embodiment of the sixth embodiment, but the partition plate-shaped housing slanting plate 61 is formed on the S circle surface, and the housings are formed on both sides opposite to each other through which the Y axis passes. Bearing 63, 63 and its housing bearing 63
Housing gears 62, 62 are provided on opposite outer surfaces centering on the holes, Z shaft gears 27, 27 are also provided on both shaft necks of the Z shaft 23, and intermediate gears 54, 54 meshing with them are also provided. Intervene.

The Z-axis 23 shaft neck is fitted into the housing bearings 63 and 63 and the main bearings 13 and 13 provided on the Y-axis to support the Z-axis 23 of the third embodiment. Similar to the configuration in the embodiment, both shaft arms 25, 25 formed of an arm plate having a shaft column forming a shaft neck fixed to the end of the outer surface.
And a connecting rod 26 is formed integrally with each other in a Z shape, and the shaft arms 25, 25 and the connecting rod 26 are connected to each other by the rotary piston 3.
The pivot connector 88 of the circular body element, which is accommodated in a free relation in the piston shaft hole 34 of 0, and is attached to the central portion of the connecting rod 26, is pivotally attached to the central piston pivot 35 in the rotary piston 30. In addition, each of the air chambers A, B, C, D is a housing 60.
Is a space enclosed by the inner concave surface forming the spherical surface G and the cylindrical surface of the piston intermediate shaft 33, and the arcuate surfaces 31, 41 of the skewed plate 61 of the housing. The following operation according to the configuration, and the four-stroke operation in which the working medium inflow / outflow mechanism including the ignition device Ig and each of the air chambers A, B, C, D proceed are exactly the same as the case of the embodiment of the above-mentioned mode 6. is there.

[0137]

[Embodiment 8] The embodiment 8 of the embodiment 8 is an operation mode based on the configuration of the solution means 8 and the common solution means 1 and belonging to the operation principle 2 on the geometrical figure. In this embodiment, instead of the phase plates 56, 56 made of concave plates in the embodiment of the above-mentioned embodiment 4, a phase housing 80 made of a hollow sphere is incorporated in the housing 10, and the phase housing 80 is provided. The rotary piston 30, the oblique plate 40, and the rotary main shaft 20 which are incorporated inside are formed and configured as in the embodiment of the above-described fourth embodiment.

That is, in this embodiment shown in FIG.
The inner wall surface of the housing 10 is a spherical surface G that is larger than the spherical surface G, that is, a concentric spherical surface, or a rotating surface that is concentric with the Y axis.
Housing 10 on the X-axis formed on a larger sliding contact surface
The main bearings 13 and 13 are provided so as to penetrate through the opposite walls, and in the housing 10 thus formed, a spherical inner shell having an inner surface of a spherical surface G including R and S circular surfaces is provided. The above phase housing 80 is rotatably incorporated and fitted with the X axis as a rotation axis. In this phase housing 80, housing bearings 83, 83 penetrating both opposite walls on the X-axis and an inner side surface along the extension plane of the S circle surface are machined into a circular groove having an inner diameter longer than the radius r. The orbital clearance 87 is formed, and the oblique plate ring 43 is fitted into the orbital clearance 87 to rotatably restrain the oblique plate 40.

Then, the main body bearings 13 and 13 and the housing bearings 83 and 83 provided on both sides of the X-axis line are fitted with the double-sided neck of the rotary main shaft 20 in the form of a straight axis with the X-axis line as the rotation axis line. It is inserted and supported, and like the configuration of the embodiment of the above-mentioned mode 4,
A shaft center 21 of a circular portion having a pin receiving hole located at the ball center O of the rotary main shaft 20 is pivotally attached to a piston pivot 35 of a pin-shaped column mounted in the center of the rotary piston 30, and the pin joint joint 55 is formed. To compose. On the other hand, each of the air chambers A, B, C, D includes a rotary piston 30 including an inner concave surface forming a spherical surface G of the phase housing 80 and a shaft surface of the piston intermediate shaft 33, and a skew plate 40.
It is a space that is enclosed and enclosed by both arcuate surfaces 31 and 41.

Also in this embodiment, the form 4 is used.
Of the external bevel gears, which are similar to the phase plate gears 58, 58 attached to the phase plates 56, 56 in the embodiment described above, are the outer side surfaces of the opposite sides of the phase housing 80 centered on the holes of the housing bearings 83, 83. The main shaft gear 22 having the same pitch circle diameter as that of each of the housing gears 82 is provided on both shaft necks of the rotary main shaft 20 in parallel with the housing gear 82, and an intermediate gear for reversing both of them is provided between them. If 54 is also operated, the volume changes of the air chambers A, B, C and D in the phase housing 80 show exactly the same process as in the case of the embodiment of the above-mentioned form 4.

The phase housing 80 is similar to the Z-axis housing 70 of the embodiment of the above-described fifth embodiment, inflow and outflow holes In and Ex for the working medium.
And igniter Ig are attached and operate in the same manner. That is,
The phase housing is provided with two housing flow passage holes 89, 89, 89, 89 facing the respective half-moon shaped operation chambers Ha, Ha, and the opening rotation of each of the housing flow passage holes 89. A housing flow path hole 19 having a streak length of about ½ circumference of the inner wall surface circumference is bored in the wall of the housing 10 on the circumference, and the igniter Ig is provided in each half-moon shaped operation chamber Ha. Ignition hole 86 that passes through the wall of the phase housing 80 facing the
9 and then each of the ignition holes 86 is inserted into the wall of the housing 10 on the circumference of rotation for checking the respective ignition holes 86, and at least two of them are inserted at right angles to each other, or the phase housing 80 or the skewed plate 40. Then, the required number of them are embedded and attached.

Also in this embodiment configured as described above, the rotation of the rotary main shaft 20 and the phase housing 80 by 90 degrees changes the air chamber volume of each air chamber A, B, C, D to the maximum. , The working medium inflow and outflow holes In and Ex are opened and closed in synchronization with the volume changes of the air chambers A, B, C and D. That is, if each casing flow passage hole 89 is connected to the housing flow passage hole 19 provided along with the rotation of the phase housing 80, any of the air chambers A, B, C, D corresponding to the connection space sucks, Exhaust hole I
Either n or Ex is opened to perform either intake or exhaust stroke, and if the connection is over, either compression or expansion stroke is performed. It should be noted that the ignition of the working medium by the igniter Ig is synchronized with the maximum compression stroke of each of the air chambers A, B, C, D.

From the connection of the above-described construction and operation, the air chamber A shown in FIG. 62 ends the exhaust stroke and the intake stroke, and the air chamber B ends the expansion stroke and the exhaust stroke, and the air chamber C expands and strokes. D is at the rotation angle position where both compression strokes are started.
In 2, the expansion pressure of the air chamber C spreads the gap between the rotary piston 30 and the skew plate 40 to cause the rotary piston 30 to perform the primary rotation Po, which is the direction of the force, and at the same time, the phase housing 8
The rotation main shaft 20 of the output shaft is rotated by causing the secondary rotation Ne that is the opposite rotation of the primary rotation Po that changes the phase of the skew plate 40 to 0.

[0144]

[Other Embodiments] In any of the above embodiments, four comb-shaped working chambers Fu, Fu, Fu, Fu are provided with one to three comb-shaped working chambers (Fu, Fu, Fu, or F).
u, Fu, Fu), and can be configured and operated. In particular, the rotary piston 30 having a circular plate is incorporated in the housing 10 so that the four air chambers A, B,
As another form of each of the above-described forms 1 to 8 forming C and D, a rotary piston 30 made of a hemispherical substantially circular plate is incorporated in one housing 10 so as to be horizontal with respect to the rotation axis. Two air chambers A and D in a row, or air chamber B,
Two air chambers A and B which are arranged in the vertical direction with respect to the rotation axis by incorporating the rotary piston 30 of C-shaped or substantially semi-circular plate.
Each of the embodiments in which the air chambers C and D are configured will be described below with reference to the drawings.

[Form of Horizontal Two Air Chambers] This form is shown in FIG.
7, 40, 46, 51, 54, 57, 60, and 63, in each of the embodiments 1 to 8, the rotary piston 30 is formed into a hemispherical substantially circular plate, and R in the spherical surface G is
A configuration based on the common solving means 2 formed in the two comb-shaped working chambers Fu and Fu (air chambers A and D or air chambers B and C) arranged between the S circle surfaces in the horizontal direction with respect to the rotation axis. This is an example. Incidentally, the embodiment shown in FIG. 37 is a mode in which both the embodiment shown in FIGS. 35 and 36 and the embodiment shown in FIG. 40 are opposed to the embodiment shown in FIG. 39. Also, in FIG.
The embodiment shown in FIG. 44 is the embodiment of the third embodiment of FIGS. 44 and 45, the embodiment of FIG. 51 is the embodiment of the fourth embodiment of FIGS. 49 and 50, and the embodiment of FIG. 54 is the embodiment of the fifth embodiment of FIG. 57 and the embodiment shown in FIG. 57 are respectively opposed to the embodiment shown in FIG. 56, and the embodiment shown in FIG. 60 is the embodiment shown in FIG. 59, and the embodiment shown in FIG. 63. Figure 6
2 is an aspect corresponding to the example of the above-described aspect 8.

That is, in contrast to each of the embodiments of the above-described modes 1 to 8 given by each of these modes, the rotary piston 30 arranged on the R circular surface has one surface on the R circular surface. On one side, a spherical arc surface 32 that exceeds the hemisphere in the range straddling the S circle surface, and on the other side, an arcuate contour plane of the spherical arc surface 32 is formed, and the arcuate surfaces 31 and 31 whose chord sides sandwich the K axis. The substantially hemispherical shape has two arcuate surfaces 31 and 3 of the substantially hemisphere.
It is a substantially circular plate having a larger volume than a hemisphere in which the semi-embedded cylindrical piston intermediate shaft 33 is interleaved with the K axis as a mounting axis.

Further, the skew plate 40 arranged on the S circle surface
(Embodiments shown in FIGS. 37, 40, 46, 51, 54 and 63), or the housing skew plate 61 (Embodiments shown in FIGS. 57 and 60) is provided on either side of the piston intermediate shaft 33. On one side, front and back arcuate surfaces 41, 41 corresponding to the arcuate surfaces 31, 31 of the hemispherical rotary piston 30, and the piston intermediate shaft 3
A bow-shaped plate smaller than a semicircle formed by the chord side surface 42 that slidably contacts the three pillar surfaces is formed into a circular plate shape by combining with the slanting plate ring 43 in the slanting plate 40 to form a circular plate. In 61, since the arcuate contour surface side is joined to the inner surface on the S-circle surface of the housing 60 to form a partition plate inside the housing 60, the slanting plate
0, any of the housing slanting plates 61 has a window on the K-axis that is larger than a semicircle whose side is the chord side surface 42.

When the piston intermediate shaft 33 of the rotary piston 30 is inserted into the window penetrating on the K-axis along the axial direction, the hinge joint 50 composed of both pieces on the points Ka and Kb sides. Is the rotary piston 30 and the skew plate 4
0, or the rotating piston 30, the housing 60, and the housing skew plate 6
1 and 1 with the K-axis as the hinge axis. Then, the skewed plate 40 on the S-circle separates the spherical surface G in the housing 10 on both sides, or the housing skewed plate 61 forms the spherical surface G.
The inner surface of 0 is divided into both sides, and each of them forms a hemispherical working chamber Ha, Ha which forms a hemispherical space with concave surfaces facing each other. The upper rotary piston 30 is formed into two air chambers A and D or air chambers B and C that are arranged in the axial horizontal direction and are formed of a closed comb-shaped space that changes their volumes in inverse proportion to each other.

[Form of Vertical Two Air Chambers] This form is shown in FIG.
8, 41, 47, 52, 55, 58, 61, and 64, in each of the embodiments 1 to 8, the rotary piston 30 is formed into a substantially semi-circular plate, and the R and S circles inside the spherical surface G are formed. 2 comb-shaped working chambers Fu arranged between the surfaces in a direction perpendicular to the rotation axis,
It is an embodiment of a configuration based on the common solution means 3 formed in Fu (air chambers A and B or air chambers C and D). The embodiment shown in FIG. 38 corresponds to the embodiment of the first embodiment shown in FIGS. 35 and 36, and the embodiment shown in FIG. 41 corresponds to the embodiment of the second embodiment shown in FIG. 39. In addition, the embodiment shown in FIG. 47 is the embodiment of the third embodiment of FIGS. 44 and 45, the embodiment of FIG. 52 is the embodiment of the fourth embodiment of FIGS. 49 and 50, and the embodiment of FIG. 55 is the embodiment of FIG. FIG. 5 shows an example of the above-mentioned form 5 of FIG.
The embodiment shown in FIG. 8 is opposed to the embodiment shown in FIG. 56, and the embodiment shown in FIG. 61 is the embodiment shown in FIG. 59. The embodiment shown in FIG. 64 is the embodiment shown in FIG. This is a mode corresponding to the eighth embodiment.

That is, in contrast to each of the embodiments of the above-described modes 1 to 8 given by each of these embodiments, the rotary piston 30 arranged on the R-circle surface has one of the S-circle surfaces sandwiched therebetween. An arc shape formed by a spherical arc surface 32 on the side, front and back arcuate surfaces 31 and 31 forming an arcuate contour plane of the ball arc surface 32, and chord side surfaces sandwiched by arcuate chords of the front and back arcuate surfaces 31 and 31. The plate is a substantially semi-circular plate which is united with the cylindrical piston intermediate shaft 33 with the K axis attached to the chord side surface as the axis.

Further, the slanting plate 40 arranged on the S-circle surface
Alternatively, the skewed plate 61 of the housing is formed on both sides of the intermediate shaft 33 of the piston, and the front and back arcuate surfaces 3 of the substantially semi-circular rotary piston 30 are provided.
Symmetrical arcuate surfaces 41,4 smaller than a semicircle corresponding to 1,31
1, an arcuate contour surface forming the outer peripheral contour of the arcuate surfaces 41, 41, a chordal side surface 42 formed by a semicylindrical concave surface having a groove-like recess between the arcuate surfaces 41, 41 on the K axis, and bilateral arcuate surfaces. 41,4
38, 41, 47, 52, 55, a circular plate is formed from the outer sliding contact surface 45 whose back surface is the same rotation surface.
In the skewed plate 40 of each embodiment shown in 64, one circular plate having a diameter larger than the spherical surface G diameter which is formed by combining the circular skewed plate ring 43 with the arcuate contour surface of the circular plate to form the outer peripheral surface. 58 and 61, each of which is shown in FIGS.
Then, the arcuate contour surface of the circular plate is fixed to the inner surface on the S circle surface of the housing 60 to close the space inside the housing 60 in a partition shape.

When the piston intermediate shaft 33 of the rotary piston 30 is inserted into the slanting plate 40 or the chordal side surface 42 of the housing slanting plate 61 forming the groove-like concave surface along the axial direction, the points Ka and Kb are obtained. A hinge joint 50 composed of both pieces on the side connects the rotary piston 30 and the skew plate 40, or the rotary piston 30, the housing 60, and the chassis skew plate 61 with the K axis as the hinge axis. Then, the skew plate 40 on the S circle surface
Closes the concave surface forming the spherical surface G of the housing 10, or the diagonal plate 61 closes the inner concave surface of the housing 60 forming the spherical surface G to form a half-moon-shaped working chamber Ha that forms a hemispherical space. The half-moon shaped working chamber Ha is set to the rotary piston 3 on the R circle surface.
Zeros are formed in two air chambers A and B, or air chambers C and D, which are arranged in the axially perpendicular direction and are formed of a closed comb-shaped space that changes their volumes in inverse proportion to each other.

Then, the two air chambers Fu, F arranged in the above-mentioned horizontal axis are arranged.
u or any of the above-mentioned two air chambers Fu, which are vertically aligned, the working medium is sucked and compressed in the process in which the volume of each air chamber Fu increases from the minimum position, and the top dead center of the compression. When the working medium is ignited and burned in the vicinity, the arcuate surfaces 31, 41 of the rotary piston 30 and the skew plate 40, or the rotary piston 30 and the housing skew plate 61 are spread apart. In other words, the rotary piston 30 receives the expanding combustion gas pressure and receives the expanding combustion gas pressure, and the shaft center 74 (FIGS. 37, 54, 38, 55) of the rolling shaft 72 attached to the connecting rod 26 on the X-axis.
Each embodiment), or the pivot connector 8 attached to the connecting rod 26.
8 (Fig. 40, 46, 57, 60, Fig. 41, 47, 58,
61 each embodiment), or the shaft center 21 of the rotary main shaft 20.
The Z-axis 23 (FIG. 37, 40,46,5
7, 60, each embodiment of FIGS. 38, 41, 47, 58, 61) or the rotary spindle 20 (FIGS. 51, 63, 52, 6).
4) or the housing shaft 71 (FIGS. 54 and 5).
Each of the rotating shafts of the fifth embodiment) is rotated.

After all, in any of the above-mentioned two air chambers Fu, Fu, the rotation of the rotary shaft and the plate surface of the rotary piston 30 and the skewed plate 40 or the rotary piston 30 and the skewed plate 61 of the housing associated therewith. The volume changes of the two air chambers Fu, Fu formed between them, the attachment of the inflow / outflow holes In, Ex of the working medium, etc. are equal to the two air chambers of the four air chambers in each of the above-described embodiments 1 to 8. The main elements of the configuration and the operation are the same as those in the respective embodiments of the above-described modes 1 to 8.

[0155]

[Common Aspect of Embodiments of Modes 1 to 8 (θ Angle)] In any of the embodiments described above, the angle θ created when the X axis and the Y axis intersect at the spherical center O is 10 ° <θ < 60
° is the practical range, and the optimum angle is 25 ° to 35 °
Is.

[0156]

[Aspects of Embodiments of Modes 1, 2, 4, and 6 (Concave Surface of Working Chamber)] As a mode of the concave surface forming the spherical surface G of the half-moon shaped working chamber Ha, in each of the embodiments 1 and 2 shown in FIGS. Figure 41
In place of the inner wall surface of the housing 10, the skew plate ring 43 is formed to have a ring width extended to the edge of the shaft plate 24, and the widened inner circumferential surface of the skew plate ring 43 and the inner concave surface of the shaft plate 24 are formed. Or a concave surface of the shaft plate 24, the inner wall surface of the housing 10 and the inner peripheral surface of the skew plate ring 43, with the inner wall surface of the housing 10 left annularly between the shaft plate 24 and the skew plate ring 43. Or, it is formed only from the inner concave surface of the shaft plate 24 which is formed as a concave plate that is spread to the side surface circumference of the skew plate ring 43. Further, in the embodiment of the above-mentioned mode 4, instead of the inner peripheral surface of the slanting plate ring 43 in FIGS. 49 to 52, a concave plate having a large diameter of the phase plate 56 is formed, and the whole is formed on the inner surface of the phase plate 56. In the embodiment of Mode 6, the inner side surface of the housing 60, which is formed into a concave plate having a large diameter of the shaft plate 24, is retracted instead of the inner side surface of the housing 60 in FIGS. 56 to 58. Then, all of them are held on the inner surface of the shaft plate 24.

[0157]

[Aspects of Embodiments of Modes 2, 3, 6, 7 and 8 (Reversing Device)]
Although not shown in the drawing, the Z-axis gears 27, 27 are provided on both shaft necks of the Z-axis 23.
And install the skewed plate ring gear 4 on both sides of the skewed plate ring 43.
4, 44 are provided, and intermediate gears 54,
54 is engaged with them, and in each of the embodiments 6 and 7 described above, both side parts of the housing 10 are composed of the housing gear 62, the Z-axis gear 27, and the intermediate gear 54 meshing with them. 57. Two sets of reversing devices installed in FIG.
58 and the embodiment shown in FIGS. 60 and 61, only one of the both sides may be configured, and in this embodiment, there is no problem even if the reversing devices are provided on both sides. Also in the embodiment of the above-mentioned mode 8, although not shown in the figure, two sets of reversing devices, which are composed of a housing gear 82, a main shaft gear 22, and an intermediate gear 54 meshing with both of them, are provided on opposite sides of the housing 10. May be provided on only one side.

[0158]

[Aspects of Embodiments 1, 2 and 4 (Intake / Exhaust Mechanism and Ignition Tool)] As an aspect common to each of the embodiments 1, 2 and 4, the intake / exhaust mechanism and the igniter Ig are as described above. Configurations similar to those in the examples of the forms 5 and 8 are possible. That is, the above mode 1,
In each of Examples 2 and 4 (the description in parentheses is form 4),
The shaft plate 24 (phase plate 56) has two shaft plate flow passage holes 2 penetrating the inner and outer surfaces thereof in place of the skew plate flow passage holes 49 of the skew plate 40.
9, 29 (phase plate flow passage holes 59, 59) are formed, but these two shaft plate flow passage holes 29, 29 (phase plate flow passage holes 59, 5) are formed.
9), the shaft plate 24 (phase plate 56) is shown in FIGS.
The shaft plate 24 and the connecting rod 26 (rotating main shaft 20
And the phase plate 56), one is an intake hole In and the other is an exhaust hole Ex at symmetrical positions about a plane passing through both the X and Y axes which are the mounting axes of the phase plate, and the holes are formed on different rotation circles. To be done.

In this case, the housing flow passage hole 19 is a groove-like hole which is formed in the wall of the housing 10 on two rotation circles in which the shaft plate flow passage holes 29, 29 (phase plate flow passage holes 59, 59) are opened. However, the rotary piston 30 in which the groove-shaped hole in each circumference makes forward and reverse rotations, the skew plate 40, the Z axis 23, and the shaft plate 2
No. 4 (phase plate 56), the muscle length and the number of muscles change in accordance with the rotational speed of the forward and reverse directions, and the number of igniters Ig attached also changes. The intake / exhaust mechanism and the igniter Ig are attached to the rotary piston 30 and the primary rotation Po of the skew plate 40 by the Z-axis 2.
3 (phase plate 56) is satisfied only in a region of a higher speed than the secondary rotation Ne of the second rotation Ne.

For example, when the forward / reverse rotation ratio is 1: 1 (1/1), the housing flow passage holes 19 and 19 corresponding to each half-moon-shaped working chamber Ha are formed in two circles on the inner wall surface of the housing 10. Two streaks each having a semicircular length of about 1/2 of the circumference are provided so that half of the stir length (1/4 circumference length) is superposed on the same central angle of the housing 10, and at this time, the shaft plate The skew plate 40 and the rotary piston 30 also make one rotation in the opposite direction for one rotation of the phase plate 56 (phase plate 56), while each air chamber Fu is in between.
Advances four strokes. The igniter Ig at this time has an ignition hole (fuel injection hole in a diesel engine) 86 in each shaft plate 24 (phase plate 56) and two shaft plate passage holes 29, 29 (phase plate passage holes 59, 59). At least one for the air chamber A (or the air chamber C) and one for the air chamber B (or the air chamber D) are provided on the wall of the housing 10 at the position where the ignition hole 86 is checked after being provided between them. Whether they are attached at 90 ° apart from each other at the central angle,
Alternatively, the required number is embedded in the shaft plate 24 (phase plate 56) or the skew plate 40.

[0161]

[Another Mode of Embodiments of Forms 1 and 5 (Fixed Phase Gear and Rolling Gear)] In each of the embodiments of Embodiments 1 and 5 described above, although not shown, the fixed phase gear 1 mounted and fixed to the housing 10 is fixed.
4, 14 and rolling shafts 72 rolling gears 76 mounted at both ends,
76 and 76 may be one set on either side only.

[0162]

[Aspects of Embodiments 1 to 4, 6 and 7 (Ignition Tool and Flow Path Hole)] Although not shown, the ignition tool Ig is the same as the above Embodiments 1 to 4.
In addition to the insertion of the housing 10 wall, at least one piece may be embedded in the skewed plate 40 so as to face the comb-shaped working chamber Fu and embedded in the skewed plate 40. Also in the above, not only the wall of the housing 10 but also at least one comb-shaped working chamber Fu facing each comb-shaped working chamber Fu is inserted into the wall of the housing 60 in an embedded manner.

In addition, the above-mentioned modes 1 to 4 and modes 6 and 7 (the description in the parentheses is the case 60 in modes 6 and 7,
Or the housing channel hole 69), the skewed plate channel hole 49 (housing channel hole 69) and the housing channel hole 1
As another aspect of the mutual circumference of the opening where 9 and 9 are joined,
And two of the slanting plate flow passage holes 49, 49 (casing flow passage holes 69, 69) communicating with the air chamber C face each other on the same rotation circumference of the outer peripheral surface of the slanting plate 40 (casing 60). 180 degrees apart and opened, and similarly, the oblique plate flow path hole 4 between the air chamber B and the air chamber D is formed.
9, 49 (case flow passage holes 69, 69) are also opened 180 degrees apart from each other on another circumference that does not compete with the opening circumferences of the air chambers A and C. Then, the housing channel hole (1
9 and 19) × 2 is a slanting plate flow path hole 49, 49, 49, 4
9 (housing flow path holes 69, 69, 69, 69) on the inner wall surface of the housing 10 on the two rotation circumferences of the openings, the length of the streaks is about 1/4 of the circumference of the inner wall surface. A series of skew plates 4
0 (enclosure 60) two groove-shaped holes each having an intake hole In on the advance side and an exhaust hole Ex on the delay side in the rotation direction are opened. Are paralleled at the same rotation angle.

As described above, the oblique plate flow passage holes 49, 49, 4
Even if the joint circumference of 9,49 (the housing flow path holes 69, 69, 69, 69) and the housing flow path hole (19, 19) x 2 is configured to be two circumferences, its operation and function are all Oblique plate flow path holes 49, 49, 49, 49 (case flow path holes 69, 69, 6
(9, 69) is opened in one circumference and joined to the housing flow passage holes 19, 19 in the same manner as described above. In addition, in each of the embodiments 1 to 4 and the embodiments 6 and 7, the horizontal two air chambers Fu and Fu of the other embodiments are provided.
And two vertical air chambers Fu and Fu (common solution means 2 and 3) in each of the two oblique plate flow passage holes 49 and 49 (the housing flow passage holes 69 and 69), the oblique plate 40 (the housing). By opening the outer peripheral surface of 60) on different rotation circles, the two joints with the housing flow path holes (19, 19) × 2 are connected with two lines each having a quarter circumference length. It is equivalent to two circles and is the same as the above-mentioned configuration.

[0165]

[Another Mode of Embodiments of Modes 1 to 8 (Housing Channel Hole)] As another mode common to each of the above-described modes of Embodiments 1 to 8, a housing channel hole 19 formed of a groove-shaped hole (not shown) is provided. The length of the groove-shaped hole (for each of the embodiments 1 to 4 and 6 and 7 with respect to the circumference of the inner wall surface of the housing 10, about 1/4 of the circumference, each of the embodiments 5 and 8) Then, the diameter of each flow path hole (oblique plate flow path hole 49, casing flow path hole 69, housing flow path hole 89) given to the embodiment of each mode is within a range of about 1/2 circumference length). It may be a continuous hole in which circular holes are bored in series with a smaller interval. Further, in any of the continuous hole and the groove-shaped hole, the circumferential length (diameter) of the hole opening to the outer wall side of the housing 10 is free.

[0166]

[Principle of Operation] Next, the principle of operation of the spherical rotary piston engine of the present invention will be described with reference to the above-described modes 1, 2, 3, 5, 6, 7 and the mode 1 of each of the embodiments shown in FIGS.
7 (the progress of each stroke is shown in FIGS. 65 and 66), and FIGS. 33 and 34 (the progress of each stroke is shown in FIGS. 67 and 68) showing the operation of the fourth and eighth embodiments and the fourth embodiment. Based on the above description, the forward / reverse rotation ratio is 1: 1 as an example.

First, the increase / decrease of the air chamber volume in each of the air chambers A, B, C and D will be described. In the half-moon shaped operating chamber Ha formed at the double end by the skew plate 40 or the housing skew plate 61. Double-ended rotary piston 30 incorporated
When the gap between any one of the comb-shaped working chambers Fu in the same half-moon shaped working chamber Ha is expanded to increase the volume, the gap of the other comb-shaped working chamber Fu is contracted and the volume is increased. To reduce. Further, if the spaces of both the half-moon-shaped working chambers Ha and Ha are formed to have the same volume and the semicircles on both sides of the rotary piston 30 with the piston intermediate shaft 33 as the boundary are also formed to have the same volume, the skew plate 40, Alternatively, the two comb-shaped working chambers A and D sandwiching the same arcuate surface 41 of the housing slanting plate 61 or the spaces of B and C always operate by changing their volumes inversely proportionally, and the slanting plate 40, or Two comb-shaped working chambers A, C or B, D facing each other with the diagonal plate 61 sandwiched therebetween have an increasing / decreasing relationship of the air chamber volume that is always directly proportional to each other, and antagonize each other, and four combs. The stroke volumes of the shape working chambers A, B, C, D are equal.

After all, the volume of each of the comb-shaped working chambers A, B, C, D is increased or decreased by the mutual engagement of the rotary piston 30 and the skew plate 40 or the rotary piston 30 and the housing skew plate 61 which are opposed to each other. Although the gap between the plate surfaces is small, the close proximity of the plate surfaces to each other causes the contraction of the air chamber gap, which means that the volume of the air chamber decreases and the piston in the reciprocating piston engine top dead from the bottom dead center in the cylinder. Corresponding to the operation of the process toward the point,
On the other hand, the separation of the plate surfaces from each other is an increase in the volume of the air chamber due to the expansion of the air chamber gap, and corresponds to the process of the piston moving from the top dead center to the bottom dead center in the cylinder. And the skew plate 40, or the relaxation and contraction between the plate surfaces of the rotary piston 30 and the skew plate 61 of the housing are caused by the air chambers A,
The increase and decrease of the air chamber volume in B, C, and D.

Therefore, looking at both (A) in FIG. 16 and FIG. 33, the air chamber A and the air chamber C located at the position opposite to the air chamber A have a contracted air chamber space and a minimum volume. But
Air chamber B that shares the same half-moon shaped operating chamber Ha with air chamber A
Then, the air chamber D sharing the half-moon shaped operation chamber Ha on the other side with the air chamber C has the maximum volume in which the air chamber gap is expanded to the upper limit. If rotation in the arrow direction is given in each (A) of FIG. 16 and FIG. 33, each (A) to each (B),
As shown in the order of (C), (D), (E), and (F), the air chamber gap between the air chambers A and C is gradually widened, and when the volume of the air chambers A and C increases, the opposite occurs. Further, the plate surfaces of the rotary piston 30 and the skew plate 40 or the rotary piston 30 and the chassis skew plate 61 in the air chambers B and D approach each other, and the volumes of the air chambers B and D are reduced.

That is, the operation is forward / reverse rotation by 45 degrees from each (A) in FIGS. 16 and 33 (first and second rotations Po,
When Ne), the volume changes of the air chambers A, B, C, and D are intermediate, reaching the respective (D) through the respective (B) and (C), and the volumes become equal. Further, if the operation is sequentially advanced from the respective (D) to the respective (E) and (F), the air chamber spaces of the air chamber A and the air chamber C are further expanded to increase the volume, and conversely, the air chamber B. And the volume of the air chamber D is further reduced, and forward / reverse rotation of 90 degrees is performed from each (A) of FIGS. 16 and 33 to reach each (G) of FIGS. The gap is expanded to the maximum, and conversely, the air gaps of the air chambers B and D are contracted to the minimum.

Further, from each (G) to each (H),
Each of (L) in FIGS. 17 and 34 through (I), (J), and (K)
From (A) in FIGS. 16 and 33, the front and back of the rotary piston 30 are switched by performing a half rotation in which the forward and reverse rotations are 180 degrees. After all, the air chamber A and the air chamber C shown in each (A) of FIGS. 16 and 33 extend from each (A) to each (G) of FIGS. It becomes the maximum volume, and further reaches each (L) in FIGS. 17 and 34, and each has the same minimum air chamber volume as at the time of departure. On the contrary, each of the air chambers B and D is Each (A)
The air chamber space is reduced from the maximum volume shown in FIG. 17 to the minimum volume of each (G) of FIGS. 17 and 34, and further reaches each (L) of FIGS.

Further, from (A) in each of FIGS. 16 and 33 showing the volume change of each air chamber A, B, C, D to each (L) in each of FIGS. , Each (L)
Each of the air chambers A and C shown in Fig. 2 again rotates forward and backward until it reaches the minimum volume after the maximum volume, or until each of the air chambers B and D again reaches the maximum volume after the minimum volume. , The rotary piston 30 is switched back and forth again to return to the initial phase (A) of FIGS. 16 and 33.
Each forward and reverse rotation is 360 degrees (1
Rotation), and the air chambers A, B, C,
Each of D completes four strokes. Therefore, if each air chamber A, B, C, D repeats the volume change as described above, the cycle of four strokes will continue, but each air chamber A,
It is necessary to allow the working media of the supply air supplied to B, C, and D and the exhaust air discharged to flow in and out.

Here, the general combustion of the working medium and the action of the intake air and the exhaust gas in the internal combustion piston engine will be described. It takes a certain time to burn the air-fuel mixture in the combustion chamber. Ignition is performed well before the top dead center of the piston, but generally, when ignition is performed with the maximum pressure around 12 degrees (crank rotation angle) after top dead center, work loss due to this cause is minimized. Become. In other words, normally, ignition is performed around 30 degrees before top dead center, but it does not burn immediately and there is an ignition waiting time, combustion starts around 15 degrees before top dead center, and then the cylinder pressure rapidly increases. As it rises and the combustion is completed at about 10 degrees after top dead center and reaches the maximum pressure, the rotation angle position around 15 degrees before top dead center before the start of combustion is set to (A), and after top dead center after combustion end The maximum output is obtained by adjusting the ignition advance angle so that the center between (A) and (B) when the position near 10 degrees is (B) is the top dead center. Also, it takes a certain time to discharge the combustion gas, and if the exhaust valve is opened after the expansion is continued until the bottom dead center, there is no room for the cylinder pressure to sufficiently drop due to the exhaust gas injection, and there is a negative impact on the exhaust stroke. You will be forced to work. Therefore, it is better to open the exhaust valve well before bottom dead center and drop the pressure in the cylinder to near atmospheric pressure by ejecting the exhaust gas to move to the exhaust stroke, and also consider the inertia of the high-speed intake air flow during intake. The closing timing of the intake valve is considerably delayed from the bottom dead center (a few tens of degrees in crank rotation angle). That is,
At the valve timing of opening and closing the valve, the intake valve opens well before top dead center and closes well after bottom dead center, and similarly the exhaust valve opens well before bottom dead center and close well after top dead center. The working angles of the intake and exhaust valves largely overlap at the top dead center.

However, each stroke of one cycle in the embodiment of the forward / reverse rotation ratio of 1: 1 (1/1), which is the reference in the present invention, includes the Z-axis 23 instead of the crankshaft, the housing shaft 71, or the rotating main shaft 20 ( Hereinafter, those rotary shafts will be generally referred to as engine shafts) and the intake action starts at a rotation angle of 0 degree, the intake stroke ends at 90 degrees, and the compression stroke starts, and the compression stroke ends at a rotation angle of 180 degrees. At that time, the compressed working medium is ignited to start the expansion stroke, and the expansion stroke ends at the rotation angle of 270 degrees and simultaneously starts the exhaust stroke, and the exhaust stroke ends at the rotation angle of 360 degrees. It shall be. Therefore, the comb-shaped working chamber Fu in the present invention
Change from the minimum to the maximum or from the maximum to the minimum at every 90 degrees of the engine shaft rotation angle, and the full operation of the 4-stroke cycle from the intake stroke to the compression, expansion, and exhaust stroke is a 2-stroke reciprocating piston engine. Similarly to, 360 degrees, that is, during one rotation of the engine shaft.

The flow passage hole which is a passage for the working medium is oblique to the housing flow passage hole 19 penetrating the wall of the housing 10 at a proper position for intake and exhaust of the air chambers A, B, C and D. The slanted plate passage hole 49 penetrating the plate 40 is provided as a slanted plate passage hole 49 (a casing passage hole 69 in each of the embodiments of the modes 6 and 7, and a casing passage hole 89 in each of the embodiments of the embodiments 5 and 8), and each air chamber A , B, C, D are appropriately connected as the respective strokes progress. That is, during the exhaust stroke of each of the air chambers A, B, C, D, the oblique plate passage hole 49, the housing passage hole 69, or the housing passage hole 89 is connected to the exhaust hole Ex of the housing passage hole 19. Then, the combustion gas is discharged, and at the time of the intake stroke, it is removed from the connection with the exhaust hole Ex and is connected to the intake hole In to intake fresh air.

Further, either the wall of the housing 10 which checks the inside of the void volume chamber (the combustion chamber where the piston is at the top dead center position) around which the volume of each air chamber A, B, C, D becomes minimum with the operation, or Skew plate 40 (Z-axis housing 70 in the embodiment of form 5, form 6,
No. 7 in each of the embodiments, the ignition device Ig in the case 60 in the embodiment of mode 8 and the phase housing 80 in the embodiment of mode 8 or the fuel injection valve in the mode of the diesel engine is inserted, and the air chambers A, B, C, D are inserted. In the vicinity of when the compression stroke reaches the maximum, the ignition device Ig ignites the fuel or the fuel injection valve injects the fuel to burn the air, thereby sucking the intake air in the internal combustion piston engine, compressing the intake air, and compressing the intake air. Each process of combustion, expansion, and exhaust of exhaust air is established.

[0177]

[Progress of stroke] Next, the progress of each stroke of intake, compression, expansion, and exhaust performed by each of the air chambers A, B, C, and D one after another,
Based on FIGS. 65 and 66 showing the operation of the embodiment of the first aspect in the respective embodiments of the first, second, third, fifth, sixth and seventh aspects, the implementation of the fourth aspect in the respective examples of the fourth and eighth aspects. Based on FIGS. 67 and 68 showing the operation of the example, both the forward / reverse rotation ratio 1:
1 (1/1) will be described as an example. 65, 66,
67 and 68, the operation of the embodiments of the respective embodiments is performed by the air chambers A, B, in one rotation of the rotary piston 30 and the skew plate 40 (in the embodiment of the sixth and seventh embodiments, the frame skew plate 61). C, D
It shows the change in volume.

First, in each of (a) in FIGS. 65 and 67, the air chamber A has finished the discharge of the combustion gas and the intake hole I
Although n is at the position of the start of air supply corresponding to the opened top dead center, the air chamber B undergoes the expansion stroke to the full stroke volume and the exhaust hole Ex is opened to start discharging the combustion gas. Is the start of contraction. In that respect, the air chamber D is at the end of the intake stroke in which the air chamber gap is expanded, and the air chamber C is at the position where the working medium at the upper limit of the compression stroke has already been ignited. The combustion heat and the expansion pressure of the compression medium in the air chamber C act on the plate surfaces of the rotary piston 30 and the skew plate 40, or the rotary piston 30 and the housing skew plate 61, which form the air chamber C, so that they are mutually affected. Spread the space between the plates.

That is, the expansion stroke of the air chamber C expands its own air chamber gap, and instead of the air chamber B which has already completed the expansion stroke, a rotational force is applied to the engine shaft, and FIGS.
As shown in the order of (a) to (b) and (c), the air chamber gap of the air chamber A at the opposite position of the air chamber C is also expanded, and, on the contrary, each of the air chambers B and D is expanded. It acts to reduce the air space. After all, in each of (a) of FIGS. 65 and 67, the air chamber A is the intake stroke, the air chamber B is the exhaust stroke, and the air chamber D is the compression stroke with respect to the air chamber C that starts the expansion stroke.
Although each is in the early stage of the process,
When each (i) of 5,67 goes through each (b), each (c), and each (d), it means that the air chambers A, B, C, D overlap. Do not finish one stroke at a time.

That is, the air chamber A reaches each (d) in which the air chamber space is expanded to the maximum volume, ends the intake stroke, and faces the next compression stroke, and the air chamber B reaches the minimum volume (d). ) Is reached and the next intake stroke is started, the air chamber C expands the air chamber void to the full stroke, and is connected to the exhaust hole Ex at the end of the expansion stroke, and the air chamber D contracts the air chamber space most. With the end of the compression work, the working medium is in the ignited position. The expansion pressure in the expansion stroke of the air chamber D expands the air chamber gap of the air chamber D and also expands the air chamber gap of the air chamber B at the opposite position, and conversely, the air pressures of the air chambers A and C are increased. 65 and 6 because the chamber gap is contracted and the air chamber C that has completed the expansion stroke is converted into the rotational force of the engine shaft.
In each (d) of 7, air chamber A is the next stroke.
The compression stroke, the intake stroke in air chamber B, and the exhaust stroke in air chamber C are performed.

Then, in each (g) of FIGS. 66 and 68 arriving from each (d) via each (e) and each (f), each of (a) of FIGS. The air chambers A, B, C, D rotate exactly 180 degrees to complete the operation of two strokes each, but in each (g), each of the air chambers A and B sucks and exhausts. The air chamber C is disconnected from the connection with the holes In and Ex, on the contrary, the air chamber C starts to be connected to the intake hole In, and the air chamber D follows the air chamber C and is connected to the exhaust hole Ex.
That is, the air chamber C is at a position where the intake stroke starts at the end of the exhaust stroke, and the air chamber content is almost empty, and the air chamber B whose air chamber space has been expanded by the intake starts the compression stroke, The air chamber D finishes the expansion stroke and starts exhausting exhaust air.
At this time, the compressed air in the air chamber A is ignited, and the expansion stroke of the air chamber A replaces the previous air chamber D to give a rotational force to the rotary piston 30 and the engine shaft, and at the same time, the air chamber void of the air chamber C. Is expanded to reduce the air chamber voids of the air chambers B and D.

Further, when each (G) in FIG.
Both expand the air chamber space to have the maximum volume, but in the air chamber A, the expansion work has already ended and the exhaust hole Ex is connected to discharge the exhaust air, and in the air chamber C, the stroke volume is sucked up to the full volume. Start compressing the working medium. On the other hand, air chamber B and air chamber D
Both contract the air chamber space to the minimum, but the air chamber B starts the expansion stroke by igniting the working medium having the maximum compression, and the air chamber D starts the intake stroke after starting the intake stroke after exhausting the exhaust air. Connect to In. After all, the air chambers A, B, C and D are shown in FIGS.
When each (a) of is drawn out to reach each (nu) of FIGS. 66 and 68, it means that it has rotated 270 degrees (90 degrees × 3).
In this case, one stroke is completed in the rotation of 90 degrees, so that each of the air chambers A, B, C and D has completed three strokes.

In addition, the expansion work of the air chamber B in each (nu) causes each of the air chambers A, B, C, and D to be the starting point through each (le) and each (wo). By making one round to the position (a), the rotary piston 30 and the skew plate 40
(Or the diagonal board 61) and the air chambers A, B, C, D have made one rotation (90 degrees x 4), but each air chamber A,
B, C, D completes one cycle of four strokes, and the chained expansion pressures of the four air chambers A, B, C, D act on the rotary piston 30, and the Z axis 23 or the housing axis 71, Alternatively, the engine shaft of the rotary main shaft 20 is rotated. That is, each air chamber A,
B, C, and D from (a) of FIGS. 65 and 67 to FIGS.
If the intake, compression, expansion, and exhaust strokes are repeatedly circulated in each of the above (i), the engine shaft will always receive the rotational force.

[0184]

Torque Generation Principle The torque generation in the spherical rotary piston engine of the present invention can be considered in the same manner as in the conventional reciprocating piston engine. Further, in the present invention, similarly to the conventional reciprocating piston engine, the combustion time of the working medium (in this case, the air-fuel mixture) is considerably short in the combustion chamber, and the combustion is roughly performed under a substantially constant volume. The pressure of the combustion gas corresponding to the ratio of the combustion mass is the arcuate surface 31 of the rotary piston 30.
To exert a force on the rotary piston 30 itself. That is, since the rotary piston 30 moves in the direction of the force while receiving the force due to the expanding combustion gas pressure, this force works, and in each of the embodiments 1, 2, 3, 6 and 7, the Z-axis 2 is used.
3, in the embodiment of the above-mentioned mode 5, the housing shaft 71, the above-mentioned mode 4,
In each embodiment of No. 8, the rotary main shaft 20 is converted into mechanical energy by the rotation of each engine shaft. Here, the principle of torque generation in the spherical rotary piston engine of the present invention is shown in FIG. 6 in each of the embodiments 1, 2, 3, 5, 6, and 7.
9 and in each of the embodiments 4 and 8 described above with reference to FIG. 70, the forward / reverse rotation ratio is set to 1: 1 (1/1).

That is, regarding the gas pressure Pg applied to the arcuate surface 31 of the rotary piston 30 including the cylindrical surface of the piston intermediate shaft 33, the axis lines X and Y move the same distance in the same direction from the spherical center O and intersect the spherical surface G. In a circumference having a diameter between two points P and Q (revolution locus of the L axis of the rotary piston 30), the cutting force Ft acting in the cutting direction of the circumference and the engine shaft (forms 1, 2, 3) , 6 and 7 in the embodiment, the Z axis 23 in the embodiment of the fifth embodiment, the housing shaft 71 in the embodiment of the fifth embodiment, and the Pb acting as the bearing load of the shaft neck journal in the embodiment of the fourth and eighth embodiments. You can think about it. That is, X
The pivot portion of the pin joint joint 55 with the M axis on the axis as the connecting shaft corresponds to the crank pin portion of the reciprocating piston engine, and the hinge of the hinge joint 50 at both ends (point Ka, point Kb) of the K axis. The pin 51 corresponds to the piston pin position of the reciprocating piston engine, and the connecting portion between the pin joint joint 55 and the hinge joint 50 both swings at an angle of ± θ.

Further, in each of the embodiments 4 and 8, as shown in FIG. 70, the pin joint joint 55 on the M-axis, the hinge pin 51 at both ends of the K-axis (point Ka, point Kb) and the rotary piston 30. Since the center point of the opening of the piston through-hole 34 (the point where the L axis intersects the spherical surface G) moves with the rotation by an equal distance of the angle θ, the same radius as the point P on the L axis. Even if it is considered that the center of the opening of the piston shaft hole 34 located above corresponds to the crank pin of the reciprocating piston engine, it does not change at all. Further, FIG. 69 showing each example of the above-mentioned modes 1 to 7 except the example of the above-mentioned mode 4
In FIG. 70 showing the embodiments of the above-mentioned Embodiments 4 and 8, the point Q on the Y-axis corresponds to the crank rotation center of the reciprocating piston engine. At that time, the output shaft torque T can be obtained by taking the crank pin of the reciprocating piston engine and the rotational eccentric amount of the rotary piston 30 (diameter of the revolution trajectory of the L axis, between points P and Q) corresponding to the crank radius (e) as e. , T = Ft · e.

[0187]

[Output Calculation] Therefore, 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 revolutions of the engine shaft (rpm) i: number of cycles per one revolution of the engine shaft z: number of working chambers T: torque (kg / m) In the spherical rotary piston engine of the present invention, the forward / reverse rotation ratio is When set to 1: 1 (1/1), the engine shaft (form 1,
In each of the examples 2, 3, 6 and 7, the Z-axis 23, in the example of the form 5, the housing shaft 71, and in each of the examples of the forms 4 and 8, the main shaft 20) rotates once for one expansion stroke. , I = 1/1.

[0188]

[Forward / Reverse Rotation (Embodiments of Modes 6 and 7 and Embodiments 2, 3 and 4)] In each of Embodiments 6 and 7 described above, the Z-axis 23, the rotary piston 30, and the housing 60 that rotate in opposite directions are provided. The forward / reverse rotation ratio of: is 1: other than 1: 1 (1/1) described above.
Except for 2 (1/2), 1: 3 (1/3), 1: 4 (1 /
4), 1: 5 (1/5), 1: 6 (1/6), 1: 7
It is possible to change to a region where the rotation ratio of the Z axis 23 is high, such as (1/7).

The mode of changing the forward / reverse rotation ratio in each of the embodiments of modes 6 and 7 has the same basic elements for setting the configuration in each of the modes 2 to 4 described above. The description is common to the respective embodiments of the above-described modes 2 to 4, and in that case, the configuration names of the respective examples of the modes 2 to 4 may be replaced with the configuration names in parentheses. That is, the housing gear 62 (the oblique plate ring gear 44 in each of the embodiments of modes 2 and 3, the main shaft gear 22 in the example of the mode 4), the Z-axis gear 27 (the phase plate gear 58 in the example of the mode 4), Z-axis 23 (the phase plate 56 in the embodiment of the form 4), the housing 60 and the skewed plate 61 of the housing (the skewed plate 40 in each of the embodiments of the embodiments 2, 3 and 4), the housing flow path hole 6
9 (oblique plate flow path hole 49 in each of the embodiments of modes 2, 3 and 4)
Is that.

For example, when the forward / reverse rotation ratio is 1: 3 (1/3), the casing gear 62 having a pitch circle diameter three times as long as the pitch circle diameter of the Z-axis gear 27 is formed, and is described above. Z as in the case of the configuration at the forward / reverse rotation ratio of 1: 1 (1/1)
An intermediate gear 54, which meshes with the shaft gear 27 and the housing gear 62 to rotate in a fixed axis, is interposed. That is, FIGS. 42 and 43 in the embodiment of the second aspect, and FIG.
8, the skew plate ring gear 44 having a pitch circle diameter three times longer than that of the Z-axis gear 27 is formed. The main shaft gear 22 having a double length pitch circle diameter is formed, and an intermediate gear 54 meshing with the both is interposed.

Forward / reverse 1: 3 (1 /
With the rotation ratio of 3), the Z axis 23 has 135 degrees (45 degrees x 3).
When the rotation of 30 minutes is given, the rotation piston 30 reverses the rotation of 45 degrees, and the gap between the rotation piston 30 and the skewed plate 61 of the housing shows the maximum change. That is, the rotary piston 30 moves in the conical locus U.
When the ratio of the Z-axis gear 27 and the housing gear 62 is 1: 1, one rotation of the primary rotation Po rotating above is completed every 90 degrees of rotation of the rotary piston 30. Since the gear ratio ends every 45 degrees, each air chamber Fu completes one stroke every 45 degrees of rotation of the rotary piston 30, and one rotation of the rotary piston 30 (45 degrees x 45 degrees x
In 8), each air chamber Fu advances for eight strokes.

At that time, in the presence of the four air chambers A, B, C, D, the two enclosure flow passage holes 69, 69 communicating with the respective half-moon-shaped working chambers Ha are rotated in the same rotation with a central angle of 135 degrees. Opened on the outer peripheral surface of the housing 60 on the circumference, both half-moon shaped working chambers H
Two a and Ha parts open on different rotation circles on the outer peripheral surface of the housing 60. Then, the housing flow path holes 69, 69, 6
Housing 10 on two rotating circumferences with openings 9 and 69
On the wall, housing channel holes (In, Ex) × 2, (I
n, Ex) × 2 on any circumference, one of the groove-shaped holes connected with each other having about 1/8 circumference length of the inner wall surface circumference of the housing 10 is connected to the intake hole In (in the rotation direction of the housing 60). Two lines having the leading side) and the other as the exhaust hole Ex (the trailing side in the rotation direction of the housing 60) are set as one pair, and two pairs thereof are provided to face each other.
Further, in this case, the igniter Ig is arranged so that at least two of the crescent-shaped working chambers Ha are inserted into the wall of the housing 10 by checking each half-moon-shaped working chamber Ha, but they are located at an intermediate position between the housing flow passage holes (In, Ex) × 2. The housing flow passage holes 69, 69 are inserted and faced on the circumference of the opening.

Further, the forward / reverse rotation ratio is 1: 4 (1 /
In the configuration of 4), each air chamber Fu advances one stroke for each rotation of the rotary piston 30 every 30 degrees, and each rotation (30 degrees × 12) causes each air chamber Fu to travel for 12 strokes. To do. At that time, the two housing flow passage holes 69, 69 communicating with the respective half-moon-shaped working chambers Ha and opening in the same circumference are separated from each other by approximately 150 degrees at the central angle of the housing 60, and on the same rotation circumference. Housing channel holes (In, Ex) x 3
Is a groove-shaped hole in which two streaks each having a circumferential length of about 1/12 of the circumference of the wall surface of the housing 10 are set as one pair, and three pairs thereof are formed at equal intervals, and the igniter Ig is As for each half-moon-shaped working chamber Ha, three are inserted at equilibrium intervals.

In addition, to describe the case where the forward / reverse rotation ratio is 1: 5 (1/5), each air chamber Fu advances one stroke for each rotation of the rotary piston 30 every 22.5 degrees. 1 rotation (2
At 2.5 degrees × 16), each air chamber Fu performs 16 strokes. At that time, the two housing flow passage holes 69, 69 communicating with the respective half-moon-shaped working chambers Ha and opening on the same rotation circumference are opened on the same rotation circumference with an interval of about 157.5 degrees from each other. Housing channel hole (In, Ex) x 4 is approximately 1 /
Four pairs of groove-shaped holes each having two circumferential lines of 16 circumferences are formed at equal intervals, and the igniter Ig has four pieces for each half-moon-shaped working chamber Ha. Insert at intervals. Further, the forward / reverse rotation ratio is 1: 6 (1/6), 1: 7.
Also in (1/7), ..., the configuration of each part corresponding to the forward / reverse rotation ratio may be configured.

[0195]

[Forward / Reverse Rotation (Embodiments of Forms 5 and 8 and Forms 1, 2 and 4)] In each of Embodiments 5 and 8 above, although not shown, the Z-axis housing 70 and the rotary piston 30 (implementation of Form 5) Example), or the forward / reverse rotation ratio of the phase housing 80 and the rotary piston 30 (embodiment of mode 8) is 3: 1 (3/1) including 1: 1 (1/1), 5: 1 (5 / 1), 7: 1 (7 /
1), 9: 1 (9/1), and so on, even if the rotational piston 30 is changed to a higher rotational speed than the Z-axis housing 70 and the phase housing 80, one cycle and four strokes continue. It is possible to operate it.

Further, in each of the embodiments of the above-described modes 1, 2 and 4, as described above in the other mode (intake / exhaust mechanism and igniter) of the embodiment of modes 1, 2, and 4, In each of the embodiments, the shaft plate passage holes 29, 29 are formed in the shaft plate 24, and
In the embodiment, if both the phase plate flow passage holes 59, 59 are provided in the phase plate 56 to cope with the operation, the operation by changing the forward / reverse rotation ratio is performed as in the case of each of the embodiments 5 and 8. It is possible. In the following, the configuration and the suction and exhaust holes In and Ex associated with the change in the forward / reverse rotation ratio in each of the embodiments of the fifth and eighth embodiments, including the embodiments of the first, second, and fourth embodiments, and the ignition tool Ig that is inserted and attached.
Will be described on the basis of the rotation ratio of 1: 1 (1/1), but the names in parentheses are for each of the embodiments 1, 2 and 4.

In this forward / reverse rotation mode, even if the ratio of forward / reverse rotation is changed, the casing flow passage holes 89, 89 (the shaft plate flow passage holes 29, 2) that open toward the same half-moon shaped operation chamber Ha are formed.
9, two of the phase plate flow path holes 59, 59) are provided in the Z-axis housing 70.
In the case of the housing shaft 71 and the rolling bearing 73, in the case of the phase housing 80, the orbital gap 87 and the housing bearing 83 (the shaft plate 24 and the connecting rod 26, the rotary main shaft 20 and the phase plate 56) are both attached to the axes X and Y.
One is an intake hole In and the other is an exhaust hole Ex. The housing flow path hole 19 includes the housing flow path holes 89, 89 (the shaft plate flow path holes 29, 29, the phase plate flow path hole 5).
Housing 1 on two rotating circumferences with openings 9 and 59)
Although it is a groove-shaped hole that pierces the 0 wall, the muscle length and the number of muscles in the same circumference change as follows according to the ratio ratio of forward and reverse rotations.

Incidentally, the forward / reverse rotation ratio described above is 1: 1 (1 /
In the setting of 1), the housing flow passage holes 19 facing the half-moon-shaped working chambers Ha of the air chambers A and B are provided in two circles of the wall of the housing 10 with one line having a circumferential length of approximately ½ of each circle. Open half of each muscle length (1/4 circumference length) at a position where they overlap at the same central angle of the housing 10, and both half-moon shaped operation chambers Ha, H
Both sides are parallel to the same central angle position in the portion a, but the advancing side of the skew plate 40 in the rotation direction of these two streaks is the intake hole In,
The lagging side is the exhaust hole Ex, and half the muscle length of each leading side is connected to the air chamber A, and the half muscle length of each lagging side is connected to the air chamber B. Further, at this 1: 1 (1/1) forward / reverse rotation ratio, the skew plate 40 and the rotary piston are rotated with respect to one rotation of the Z-axis housing 70 and the phase housing 80 (the shaft plate 24 and the phase plate 56). 30 also makes one revolution, during which each air chamber Fu operates for four strokes.

On the other hand, the forward / reverse rotation ratio is 3: 1 (3 /
The housing flow passage holes 19 facing the half-moon-shaped working chambers Ha of the air chambers A and B in 1) are formed on each of the two circumferences of the wall of the housing 10 by approximately 1/4 of the circumference. The muscles are opposed to each other 180 degrees apart from each other, and four muscles are provided along two circles. The opposing two muscles are overlapped with each other by a half-muscle length on the same rotation angle and separated from each other by 45 degrees, and the two opposing muscles on the advancing side of the rotation of the skew plate 40 have exhaust holes Ex,
Ex, the lagging side is the intake holes In, In, and the muscle lengths corresponding to half of the leading side of each are connected to the air chamber A,
Half of each delay side muscle length is connected to the air chamber B.
In the forward / reverse rotation ratio of 3: 1 (3/1), the skew plate 40 and the rotary piston 30 are rotated with respect to one rotation of the Z-axis housing 70 and the phase housing 80 (the shaft plate 24 and the phase plate 56). Is 3
While rotating, each air chamber Fu advances by eight strokes.

When the forward / reverse rotation ratio is 5: 1 (5/1), the housing flow passage holes 19 facing the half-moon-shaped working chambers Ha of the air chambers A and B are generally formed on each of the two circumferences. 1/6
Three streak-shaped holes, each of which has a circumference length, are drilled at equal intervals of 120 degrees apart, and three of the two circumferences.
The muscles are separated by a central angle of 30 degrees, and the muscles of three muscles are overlapped by 30 degrees at the same central angle of the housing 10. Further, each of the three lines is drilled on the advance side with respect to the rotation of the skew plate 40.
n and In, and three muscles in the same circumference that are drilled on the lag side are exhaust holes Ex, Ex, Ex, but the front half on the leading side for each muscle length is connected to the air chamber A, The rear half of the delay side is connected to the air chamber B. In the forward / reverse rotation ratio of 5: 1 (5/1), the skew plate 40 and the rotary piston 30 are rotated with respect to one rotation of the Z-axis housing 70 and the phase housing 80 (the shaft plate 24 and the phase plate 56). Rotates 5 times, at which time each air chamber Fu completes 12 strokes.

When the forward / reverse rotation ratio is set to 7: 1 (7/1), the housing flow passage hole 19 has approximately 1/8 of each circumference.
Four streaks each having a circumferential length are equally spaced at intervals of 90 degrees, and eight streak-like holes are provided along the two circumferences. At that time, the Z-axis housing 70 and the phase housing 80 (the shaft plate 2
4, the skew plate 40 and the rotary piston 30 rotate 7 times for one rotation of the phase plate 56), during which each air chamber Fu completes 16 strokes. The forward / reverse rotation ratio is 9: 1 (9 /
In the case of 1), the housing flow path hole 19 has five lines (10 in 2 circles) each having a circumference length of approximately 1/10 in each circle.
Groove) hole is provided, and the skew plate 40 and the rotary piston 30 rotate 9 times for one rotation of the Z-axis housing 70 and the phase housing 80 (the shaft plate 24 and the phase plate 56), and in between, Air chamber F
u completes 20 strokes each.

Further, the forward / reverse rotation ratio is 11: 1 (11/1).
The housing flow passage holes 19 in each of the
/ 12 circles are provided with 6 lines (12 lines in 2 circles), and the skew plate 40 and the rotary piston are included in one rotation of the Z-axis housing 70 and the phase housing 80 (the shaft plate 24 and the phase plate 56). 30 is 1
One rotation is performed, and each air chamber Fu performs 24 strokes. Less than,
Forward / reverse rotation ratio is 13: 1 (13/1), 15: 1 (15 /
1), 17: 1 (17/1), and so on, the housing channel hole 19 has a shorter streak length, and the streak number is configured in a larger range to increase the number of strokes performed by each air chamber Fu. .

In the configuration for creating the forward and reverse rotations, for example, the rotation speed ratio is set to 3: 1 (3/1), and the fifth embodiment is adopted.
In the case of the embodiment of (or mode 1), the fixed phase gear 14 is formed on the rolling gear 76 having a diameter of 1/3 pitch and meshes with the fixed phase gear 14. If the ratio is 5: 1 (5/1), the rolling gear 7
6 is configured to have a 1/5 pitch circle diameter of the fixed phase gear 14.
Further, for example, in the case of the embodiment of the above-mentioned mode 8 (or mode 4) in which the forward / reverse rotation ratio is set to 3: 1 (3/1), the main shaft gear 22 is provided on the concentric circle of the main shaft gear 22 attached to the rotary main shaft 20. A casing gear 82 (phase plate gear 58) having a pitch circle diameter three times longer than that of the above is formed and arranged as an internal gear, and an intermediate gear 54 for rotating a fixed axis on the casing gear 82 and the main gear. It is intervened between 22 and 22 and meshes with both. Further, when the forward / reverse rotation ratio is 5: 1 (5/1), the housing gear 82 (phase plate gear 58) is formed to have a pitch circle diameter five times longer than the main shaft gear 22.

Further, for example, the forward / reverse rotation ratio is 3: 1 (3 /
In the embodiment of the above-mentioned mode 2 when set to 1), both the outer peripheral surface of the oblique plate ring 43 and the outer peripheral surface of the edge portion of the shaft plate 24 are formed into gears having the same pitch circle diameter, and An intermediate gear 54 in which two gears having a pitch circle diameter ratio of (3) to (1) are coaxially mounted and fixed, and a pitch circle diameter that meshes with the intermediate gear 54 having the pitch circle diameter (1) is free. Intermediate gear 5
4 is provided to allow bearings to be fixedly positioned on the wall of the housing 10,
Then, the intermediate gear 54 having a free pitch circle diameter is attached to the oblique plate ring 4
The gears on the outer peripheral surface of the shaft 3 are meshed with each other, and the intermediate gear 54 having the pitch circle diameter (3) of the two coaxial gears is meshed with the gear on the outer peripheral surface of the edge portion of the shaft plate 24. Or the rotation ratio is 5: 1 (5/1)
In the above, the intermediate gear 54 composed of the two coaxial gears of (3) to (1) is formed so that the pitch diameter ratio is (5) to (1).

Further, the igniter Ig has the same half-moon-shaped working chamber H.
From the ignition hole 86 opened at the intermediate position of the two housing flow passage holes 89, 89 (the shaft plate flow passage holes 29, 29, the phase plate flow passage holes 59, 59) facing the a to the end of the compression stroke. Air chamber F
Although it is attached to the wall of the housing 10 at the proper position to check the u space,
As described above, when the forward / reverse rotation ratio is 1: 1 (1/1), at least one portion of the air chamber A faces the half-moon shaped operating chamber Ha of the air chambers A and B, and one portion of the air chamber B is provided. Also, at least one of them is inserted at 90 ° apart from the center angle of the housing 10, and the same number of them are inserted so as to face the half-moon-shaped working chambers Ha of the air chambers C and D.

On the other hand, the forward / reverse rotation ratio is 3: 1 (3 /
The igniter Ig in 1) is inserted with at least two for the air chamber A and two for the air chamber B, but two of the same air chambers face each other, Two B parts are separated by 45 degrees, and the same number is similarly inserted into the air chambers C and D. Further, when the forward / reverse rotation ratio is 5: 1 (5/1), at least three air chambers A and B are inserted, and the ignition holes 86 at that time are at least two holes.
Alternatively, the igniter Ig can be freely attached by, for example, inserting the required number of the Z-axis housing 70, the phase housing 80 (the shaft plate 24, the phase plate 56), or the skew plate 40 in a buried shape. In that case, the ignition hole 86 is unnecessary.

Next, in each of the embodiments 5 and 8 in which the forward and reverse rotations are made, the Z-axis housing 70 and the phase housing 80 are rotated once and the air chambers A and B are operated for four strokes per cycle. Rotating forward / reverse rotation ratio for half-moon working chamber Ha is 1: 1 (1/1)
Will be described as an example with reference to FIG. 71. In FIG. 71, the (a) side of successive figures a, b, c, d is the intake hole In side of the air chambers A, B, and the (b) side is the air chambers A, B.
Of the exhaust hole Ex.

First, in FIG. 71a, the air chamber A is shown in FIG.
As shown in (b), the housing passage hole 1 on the exhaust hole Ex side
At the same time as it is disengaged from the connection with the casing 9, it is joined to the suction-side casing flow passage hole 89 as shown in FIG.
Further, 9 is a position corresponding to the top dead center of the piston at which joining with the intake hole In of the housing flow path hole 19 is started, so that the operation of the air chamber A from now on is an intake stroke for sucking the working medium. Further, the air chamber B is joined to the housing passage hole 89 on the exhaust hole side as shown in FIG. A (b), and the housing passage hole 89 is further joined to the exhaust hole Ex of the housing passage hole 19 of the piston. Since it is at the position corresponding to bottom dead center, air chamber B
In the exhaust stroke, the combustion gas is discharged.

Then, the rotary piston 30 and the air chambers A and B in FIG. 71 rotate clockwise (clockwise) in the direction of the arrow, and the housing flow passage holes 89 and 89 and the Z-axis housing 70 or the phase housing 80. Rotates counterclockwise (counterclockwise) as shown in Figure a.
From FIG. A to FIG.
From (a) and (b), the rotary piston 30 and the skew plate 40
Rotates 90 degrees, and at the same time, in the opposite direction, Z-axis housing 7
0, or when the phase housing 80 rotates 90 degrees, the air chambers A and B and the housing flow passage holes 89 and 89 are shown in FIGS.
At the rotation angle position shown in, the operation for one stroke is completed. In FIGS. B (a) and (b), the air chamber A is disengaged from the connection with the intake hole In of the housing flow passage hole 19 and the compression stroke is started at the end of the intake stroke, and the air chamber B is discharged from the exhaust hole E.
The joint is moved from x to the intake hole In, and the intake stroke is started.

Further, when the air chambers A and B are rotated by 90 degrees and the Z-axis housing 70 or the phase housing 80 is also rotated by 90 degrees in the opposite direction from FIGS. B (a) and (b), the air chambers are rotated by 90 degrees. A and B are operated one stroke at a time, and in the figures c (a) and (b), the air chamber A is not connected to either the intake or exhaust holes In and Ex, and reaches the top dead center. The working medium in the space is ignited to start the expansion stroke, and the air chamber B is the position where the intake air supply to the air chamber space corresponding to the bottom dead center position is finished and the compression stroke is started. When the air chambers A and B and the Z-axis housing 70 or the phase housing 80 are rotated by 90 degrees in opposite directions from each other from FIGS. C (a) and (b), the air chambers A and B are moved by one stroke each. D) and (b) in which the air chamber A is operated, the air chamber A has an air chamber space corresponding to the bottom dead center at which the expansion stroke is completed.
The exhaust stroke is started by joining to the exhaust hole Ex of No. 9, and the air chamber B is at the rotation angle position where the compressed air at the top dead center position is ignited.

Further, from FIGS. D (a) and (b), the air chambers A and B are rotated by 90 degrees, and the Z-axis housing 7 is rotated in the opposite direction.
When 0 or the phase housing 80 is also rotated by 90 degrees, the air chambers A and B are further operated by one stroke each and the operation returns to the starting point a in FIG. The air chamber A in which the air chamber space is changed from the maximum volume to the minimum volume is joined to the exhaust hole Ex of the housing flow passage hole 19 to end the exhaust stroke, and the air chamber closed by the inoperative casing flow passage hole 89. The air chamber B whose space is changed from the minimum volume to the maximum volume ends the expansion stroke. Eventually, the original figure a (a) is passed through the figures a (a) and (b) through the respective a (b), c, and d (a) and (b).
Returning to (B), the air chambers A and B, the rotary piston 30, and the skew plate 40 rotate 90 degrees × 4 times (one rotation), and in the opposite direction, the Z-axis housing 70 or the phase housing 80. 90 degrees x 4
Each time (one rotation), the air chambers A and B complete four strokes of intake, compression, expansion, and exhaust.

Therefore, the expansion stroke for generating the torque is
If four air chambers A, B, C, and D are configured by adding air chambers C and D, in one cycle returning from FIG. 71a to FIG. The air chamber C which is not operated is performed, the air chamber D which is not illustrated in FIG. B is performed, and the air chamber A illustrated in (c) in FIG. C is performed, and the air chamber B illustrated in (a) is illustrated in FIG. Therefore, this form 5,
In the embodiment in which the forward / reverse rotation ratio is 1: 1 (1/1) in each of the eight examples (the same applies to modes 1, 2, and 4), if four air chambers A, B, C, and D are present. The engine rotation force continues. In addition, the form having the forward / reverse rotation ratio is
In the case of carrying out in each example of No. 4, the Z-axis housing 7
0, instead of the two casing flow passage holes 89, 89 for each half-moon shaped working chamber Ha in the phase casing 80, two shaft plate flow passage holes 29, 29 in each shaft plate 24, or two in each phase plate 56. If the through holes are opened in both the phase plate flow path holes 59, 59, the following configuration and operation are the same as those in the respective embodiments of the above-mentioned modes 5 and 8.

Next, as another example, the Z-axis housing 70,
Alternatively, the forward / reverse rotation ratio of 3: 1 (3/1) when the rotational speeds of the rotary pistons 30 and the skew plates 40 applied to the respective phase housings 80 are higher than the rotational speeds of the phase housings is set to 3: 1 (3: 1). The air chambers A and B in FIG. 7 are configured to correspond to the half-moon-shaped working chamber Ha, and one rotation of the phase housing 80 will be briefly described below with reference to FIGS. The forward / reverse rotation ratio is 3: 1 (3 /
72 (a) to 73 (h) showing the four strokes of 1), the continuous diagram on each side (a) shows the intake holes In and In, and the continuous diagram on each side (b) shows the exhaust holes Ex, Ex. Also, from each figure to the next figure, the air chambers A and B, the rotary piston 30, and the skew plate 40 are rotated by 135 degrees at the rotation angle, and at the same time, the phase housing 80 is rotated in the opposite direction. Since the rotation is 45 degrees, the operation returning from FIG. A to FIGS. B to h to FIG. A again is three rotations of 135 degrees × 8 rotations of the rotary piston 30 and the air chambers A and B, and 45 degrees of housing 80 ×
One rotation, which is eight times, corresponds to the amount that each of the air chambers A and B ends eight strokes.

72a (a), (b) to b (a),
In the operation up to (b), the air chambers A and B rotate 135 degrees, which corresponds to one stroke, and the phase housing 80 rotates 45 degrees in the opposite direction, and mediates through the housing flow passage holes 89 and 89. Both are joined to the housing flow passage hole 19 of one of the two streaks, but as shown in FIGS.
The air chamber A joined to the rear half is the intake stroke, and the air chamber B joined to the front half of the exhaust hole Ex is the exhaust stroke, as shown in FIGS. From there air chambers A and B are 135
Figure b (a), (b) to c below
In the operations leading to (a) and (b), the air chamber A is the compression stroke in the closed space, and the air chamber B is from FIG. B (a) to FIG. C (a).
This is the intake stroke of joining to the intake hole In.

Each of the air chambers A and B in FIGS. C (a) and (b) is further rotated by 135 degrees, and thus, in FIGS. D (a) and (b).
In the operation shown up to, the air chambers A and B both suck and the exhaust holes In,
Ex is not connected to the housing flow passage holes 19 and 19 and is closed, and the air chamber A is the ignited expansion stroke and the air chamber B is the compression stroke in FIG. Further, each of the air chambers A and B is rotated by 135 degrees, which corresponds to one stroke, and is rotated as shown in FIG.
The operation from (a), (b) to FIG. 73e (a), (b) is performed by the air chamber A as shown in FIG. D (b) to FIG. 73e (b). The exhaust stroke is ended by joining with the hole 19, and the air chamber B ends the expansion stroke in the space where the ignited working medium is closed in FIG.

The air chambers A and B which reach this FIG. 73e are shown in FIG.
From a, it makes one and a half rotations of (135 degrees x 4), and the phase housing 80 also makes a half rotation of (45 degrees x 4) in the opposite direction to the air chambers A and B, during which each air chamber A, B Complete one cycle of 4 strokes each. And that figure e (a), (b)
As shown in FIGS. F (a) and (b), if the air chambers A and B further rotate 135 degrees and the phase housing 80 rotates 45 degrees in the opposite direction, the air chamber A again Performs an intake stroke and air chamber B performs an exhaust stroke. From there, air chamber A,
Rotation of 135 degrees to B and 45 degrees to the opposite direction to the phase housing 80 in the opposite direction, the operation for one stroke from Figure f to Figure g (a), (b) is that the air chamber A is in the compression stroke again. Yes, the air chamber B is in the intake stroke again.

In addition, the following figures g to h (a) and (b)
The operation up to is that the air chamber A is again in the expansion stroke, the air chamber B is in the compression stroke again, and from FIG.
When the phase housing 80 rotates 45 degrees in the opposite direction,
72a (a) and (b) in which the air chamber A has completed the exhaust stroke and the air chamber B has finished the expansion stroke again and started operation. After all,
By that time, each of the air chambers A and B has performed eight strokes of two cycles, and as described above, each of the air chambers A and B has 13 strokes.
The phase is returned to the original by performing three rotations of 5 degrees × 8 times, and at the same time, the phase housing 80 rotated in the opposite direction to the air chambers A and B is also rotated once to return the phase.

[0218]

[Progression (Embodiments of Embodiments 1 to 8)] As described above, the spherical rotary piston engine of the present invention has the primary rotation Po rotating on the conical locus U and the secondary rotation N rotating on the conical trajectory J.
e is valid in a forward / reverse rotation configuration in which the forward and reverse rotations are performed, but the primary and secondary rotations Po, N are opposed to the forward / reverse rotation.
As described above, it is also possible to configure and operate e.g. forward rotations that rotate in the same direction, even though the speed ratios of e are relatively fast and slow. Next, the primary rotation Po
74 to 81 (FIG. 75 showing the embodiment of the above-mentioned embodiment 1; FIG. 75, It demonstrates based on FIG. 79 which shows the Example of the said form 6, and FIG. 74 which shows the example of the said form 8.

In the normal rotation mode, the rotary piston 30 that performs the primary rotation Po and the skew plate 40 that performs the secondary rotation Ne are the Z-axis 23, the phase plate 56, or the Z-axis housing 70.
There are operation modes that are roughly divided into cases in which the rotation speed is faster and slower than the phase housing 80. Among them, the operation mode in which the rotation speed on the primary rotation Po side, which belongs to the former case, is higher, The second, fourth, fifth, and eighth embodiments are possible, and the operation modes having a high speed ratio on the secondary rotation Ne side belonging to the latter are the above-mentioned modes 1, 2, 3, 4, 6, and 7. This is possible in the configuration of the embodiment. In addition, the forms in this normal rotation are the primary rotation Po and the secondary rotation N which have a correlation.
4 strokes of 1 cycle operate based on the lower (slower) forward rotation ratio in either of the rotation ratios of e and e. In any form, the mutual ratio is based on 1: 3 or 3: 1 age,
Below 1: 5,1: 7,1: 9,1: 11,1: 1
3, or 5: 1, 7: 1, 9: 1, 11: 1, 1
It holds even if the direction is changed to 3: 1.

[0220]

[Form in which the forward rotation ratio of the primary rotation is higher than that in the secondary rotation] Therefore, the above-described forms 1, 2, 4, 5, 8 in which the primary rotation Po can set the forward rotation ratio higher than that in the secondary rotation Ne. In each of the embodiments, as a first example, the working chamber Fu in the embodiment of the above-mentioned mode 8 is formed into four air chambers A, B, C, D which are the two half-moon shaped working chambers Ha, Ha, and 3: 1 ratio
A description will be given based on FIG. 74 configured such that (3/1 to numerator represents the rotation speed ratio of the primary rotation Po and the denominator represents the rotation speed of the secondary rotation Ne).

As shown in FIG. 74, the main shaft gear 22 of the external gear is attached to the shaft neck of the rotary main shaft 20, and the phase gear 80 also has the external gear gear 82 of the external gear having a pitch circle diameter larger than that of the main gear 22. Are mounted, and two large and small intermediate gears 54, 54 coaxially fixed on the mounting planes of the two gears 22, 82 are mounted at a fixed position of the housing 10 so as to intervene, and the larger intermediate gear 54 is toothed on the main shaft gear 22. The smaller intermediate gear 54 is meshed with the housing gear 82, and the phase housing 80 is attached to the large and small intermediate gears 54, 54.
The gear ratio is set so that the rotation speed becomes 1/3 of 0. Alternatively, although not shown, the forward turn ratio is 3: 1 (3 /
The gear device that produces 1) is a casing gear 82 of an internal gear having a pitch circle diameter three times longer than that of the spindle gear 22.
2 is attached to the phase housing 80, which is on the concentric circle, with the housing bearing 83 hole as the center, and the main shaft gear 22 and the housing gear 8
Two intermediate gears 54, 54 that rotate with a fixed axis and mesh with each other are interposed between the two, one of the intermediate gears 54 is externally meshed with the main shaft gear 22, and the other of the intermediate gears 54 is a housing gear 82. Inscribe and mesh.

In any of the above constructions, the rotary main shaft 20
Since the phase housing 80 is rotated in the same direction as and at a speed that is ⅓ thereof, the main shaft 20 is rotated for one rotation of the phase housing 80.
Rotates 3 times, and the rotation main shaft 20 rotates 3 times to rotate the rotary piston 30 and the skewed plate 40 3 times to obtain a forward rotation ratio of 3: 1.
(3/1) is established. It should be noted that in the above-described forward / reverse rotation mode, one stroke performed for a rotation of 180 degrees or less rotates at the forward rotation ratio of 3: 1 (3/1).
Of 270 degrees, the phase housing 80 rotates 90 degrees in the meantime. Therefore, 1 of the phase housing 80
The rotation and the three rotations of the rotary piston 30 correspond to the four strokes of intake, compression, expansion, and exhaust, respectively.
The air chamber voids of C and D are changed by 4.

In this case, although not shown in the figure, the phase housing 80 is provided with two housing flow passage holes 89, 89 for the respective half-moon operating chambers Ha, but two for each half-moon operating chamber Ha. Is X, which is the axis of formation of the housing bearing 83 and the orbital gap 87,
One is an intake hole In and the other is an exhaust hole Ex, which are opposed to each other with a plane passing through the Y-axis line as a center plane and on different rotation circumferences. Both half-moon working chambers H
Two casing flow passage holes 89, 89 arranged in parallel for a and Ha
If one is the intake hole In, the other is the exhaust hole Ex. Further, an ignition hole (a fuel injection hole in the case of a diesel engine) 86 as an ignition port is provided between the two housing flow passages 89, 89 facing each half-moon working chamber Ha.
At least one of the opening circles 9 and 89 is opened with a difference in circumference, and two half moon-shaped working chambers Ha, two for Ha are opened at opposite positions. Eventually, the phase housing 80 has at least three holes, which are two housing flow passage holes 89, 89 and one ignition hole 86, for each half-moon-shaped working chamber Ha, and both half-moon-shaped working chambers Ha, Six holes are opened in the entire Ha part.

On the other hand, the housing flow passage holes 89, 89, 89, 89
The housing flow path holes 19, 19, 19, which are groove-shaped holes having approximately ½ circumference lengths along the circumference of the housing 10 wall on the four opening rotation circumferences 19
Among the two muscles facing the half-moon shaped working chamber Ha, the muscles on the delay side in the rotation direction of the rotary piston 30 and the phase housing 80 are bored as intake holes In and the muscles on the leading side are bored as exhaust holes Ex. However, the two muscles of the intake and exhaust holes In and Ex are half of each other's muscle length (the intake hole In is the front half and the exhaust hole Ex is the rear half).
Are placed at the same central angle of the housing 10, and both half-moon-shaped working chambers Ha, Ha are arranged in parallel at the same central angle of the housing 10,
In addition, the two muscles on the air chambers A and B are located in the air chamber B with the front half of the muscle length
The rear half is joined to the air chamber A, and the front half of the muscle length of each of the two muscles on the air chamber C and D sides is joined to the air chamber D and the rear half is joined to the air chamber C. Further, the igniter Ig uses the ignition chambers A, B, C, and D whose ignition timing has come to the ignition hole 8 of the phase housing 80.
The air chambers A, B,
At least one is inserted for each of C and D, and four are inserted in total, but two for each half-moon-shaped working chamber Ha are inserted at appropriate positions separated by 90 degrees at the central angle of the housing 10. .

As a next example, to describe the configuration of the embodiment of the above-described mode 1 with a forward rotation ratio of 3: 1 (3/1), as shown in FIG. 75, with respect to the rolling gear 76 attached to the rolling shaft 72, The fixed phase gear 14, which is an external gear having a pitch circle diameter of 3 times the length, is fixed to the wall of the housing 10 on the Y axis. In this case, the rolling gear 76 is arranged on the mounting plane of the fixed phase gear 14. When the Z-axis 23 is rotated by externally meshing with the fixed phase gear 14, the connecting rod 26 is not shown in the drawing, but the rolling shaft 72 rotatably fitted on the connecting rod 26 is also connected to the connecting rod 26. Twenty-six turns in the same direction. In other words, since the rolling shaft 72 turns in the rotational direction of the Z-axis 23 by the rolling gear 76 externally meshed with the fixed phase gear 14, at the same time, the rolling shaft 72 rotates at a speed three times as fast as that of the Z-axis 23. The rolling shaft 72 makes the same number of turns for one rotation of the shaft 23, and at the same time, the rotation piston 30 and the skew plate 40 also make three rotations for three rotations, and the forward rotation ratio is 3: 1 ( 3/1) is established.

Here, the half-moon-shaped working chamber in which the air chambers A and B are present is taken as an example of the operation of the above-mentioned mode 8 in the operation of four strokes per cycle in the configuration of the forward rotation ratio of 3: 1 (3/1). Ha
Based on FIG. 76 showing the above, description will be made for one rotation of the phase housing 80. Incidentally, (a) of a to d in FIG.
The side is the intake holes I of the air chambers A and B in the embodiment of the above-mentioned mode 8.
It is the n side, and the (b) side is the exhaust hole Ex side.

Now, the air chamber A is joined to the suction-side casing flow passage hole 89 as shown in FIG. 76a (a), and the casing flow passage hole 89 is formed.
Is a position at which joining with the intake hole In of the housing flow path hole 19 is started and is out of the connection with the housing flow path hole 19 on the exhaust side as shown in FIG. Since the rotation angle position corresponds to, the intake stroke for inhaling the working medium is started. Further, the air chamber B in FIG. A (b) is joined to the exhaust-side casing flow passage hole 89, and the casing flow passage hole 89 also starts to be joined to the exhaust passage Ex of the housing flow passage hole 19, and under the piston. The rotation angle position corresponds to the dead point, and the exhaust stroke for discharging the combustion gas is performed from this position.

At this time, the rotary piston 30, the air chambers A and B, and the phase housing 80 shown in FIG. 76 rotate clockwise in the direction of the arrow and operate in the order of FIGS. A to b, c, and d. From a, the rotary piston 30 and the skew plate 40 are 27
When the phase housing 80 is rotated by 90 degrees at the same time as it is rotated by 0 degree, the air chambers A and B and the housing flow passage holes 89 and 89 are at the rotation angle position shown in FIG. To finish.
In FIGS. B (a) and (b), since the intake hole In of the housing flow path hole 19 is out of the connection with the air chamber A and is in contact with the air chamber B, the air chamber A in FIG. Is immediately after the start of the compression stroke and the start of the intake stroke of the air chamber B.

Further, from FIG. B, the air chambers A and B correspond to 270 degrees,
At the same time, the phase housing 80 is rotated by 90 degrees in the same direction, and each of the air chambers A and B is operated one stroke at a time, as shown in FIG.
In (b), the air chamber A is not connected to any of the intake and exhaust holes In and Ex, the working medium in the air chamber space reaching the top dead center is ignited to start the expansion stroke, and the air chamber B bottoms to the bottom. The intake stroke ends and the compression stroke starts in the air chamber space corresponding to the point position. When the air chambers A and B are rotated by 270 degrees and the phase housing 80 is also rotated by 90 degrees from the state shown in FIG. (B), the air chamber A becomes an air chamber space corresponding to the bottom dead center position, ends the expansion stroke, and is joined to the exhaust hole Ex of the housing flow passage hole 19, and the air chamber B is the gas at the top dead center. Since the compressed air in the chamber space is at the rotational angle position where the compressed air is ignited, the air chamber A in FIG. 8D is immediately after the exhaust stroke and the air chamber B is immediately after the expansion stroke.

Further, the air chambers A and B are 270 in FIG.
When the phase housing 80 is also rotated 90 degrees at the same time, the air chambers A and B, which have been operated one stroke at a time, end in four strokes in FIG. Return. That is, between FIG. D and FIG. A, the air chamber A changes the air chamber space from the maximum volume to the minimum volume, and in the meantime, it joins with the exhaust hole Ex of the housing flow passage hole 19 to end the exhaust stroke, In contrast to the air chamber A, the air chamber B changes the air chamber space closed by the casing flow passage hole 89 from the minimum volume to the maximum volume to end the expansion stroke.

After all, from FIGS. A (a) and (b) to FIGS.
After returning to (a) and (b) of the original diagram after going through (a) and (b) of d, the air chambers A and B, the rotary piston 30, and the skew plate 4 are shown.
0 makes three rotations of 270 degrees x 4 times, and the phase housing 80 also makes one rotation of 90 degrees x 4 times in the same direction as the air chambers A and B, while each of the air chambers A and B inhales, Operates every four strokes of compression, expansion and exhaust. The expansion stroke in this case is
If four air chambers A, B, C, and D are constructed, in one cycle returning to FIG. A again through FIGS. A to d, the air chamber C not shown in FIG. The air chamber D, not shown, performs, and in FIG. C, the air chamber A, and in FIG. D, the air chamber B, so that four air chambers A, B,
C and D repeatedly generate torque.

[0232] Further, the rotation ratio of this forward rotation is 3: 1 (3/1).
In the case of carrying out the embodiment having the above-mentioned configuration in the configurations of the respective embodiments of the above-described first and second embodiments, the configuration is changed to the case flow passage holes 89, 89 for each half-moon shaped operation chamber Ha in the above-described embodiment of the eighth embodiment. If two shaft plate passage holes 29, 29 are opened in each shaft plate 24 of the Z-axis 23 at a position similar to, the following configuration and operation are similar to those of the embodiment of the above-mentioned mode 8,
Also in the case of carrying out in the embodiment of the form 4, the two phase plate passage holes 59, 59 may be similarly opened in each of the phase plates 56, and in the embodiment of the form 5, the half-moon-shaped working chamber Ha may be formed. If the two housing flow passage holes 89, 89 are provided at appropriate positions in the Z-axis housing 70, the following configuration may be the same as that of the embodiment of the above-described mode 8.

Next, as another example, the forward turn ratio is 5: 1.
(5/1) is configured for the half-moon-shaped working chamber Ha in which the air chambers A and B are present in the embodiment of the above-described mode 8, and one rotation of the phase housing 80 is based on FIGS. Explain briefly. The two housing flow passage holes 89 and 89 and the ignition hole (fuel injection hole) 8 at the forward rotation ratio of 5: 1 (5/1).
Similarly to the case of the forward rotation ratio of 3: 1 (3/1) described above, the casing 6 is provided with the casing casing flow passage holes 89, 89 formed in the phase casing 80 at positions 180 degrees apart from each other, and at the intermediate position thereof. Ignition holes 86 are provided, but the three of them have different circumferences. In that respect, the housing channel hole (19, 19) × 2 is the casing channel hole 8
Two lines of groove-shaped holes each having a circumference length of approximately 1/4 are faced to each other on each of two rotation circles where 9,89 are opened, and two lines of the two circles are opposed to each other. Each of them is pierced by penetrating through the wall of the housing 10 at the same rotation angle position where the respective half lengths of the rotation piston 30 and the phase housing 80 are overlapped.
The two lines on the leading side with respect to the rotation direction of the intake holes In, I
The exhaust lines Ex and Ex are two lines of n and the circumference on the delay side.

77 (a) to 78 (a) to 78 (h), the continuous views on the (a) side show the intake holes In, In, and the continuous views on the (b) side show the exhaust holes Ex, Ex, respectively. The operation up to the figure is the air chambers A and B, the rotary piston 30, and the skew plate 40.
Is 225 degrees, and the phase housing 80 is 45 in the same direction as those.
Since the rotation is a rotation of a degree, the operation of returning from FIG. A to FIGS. B to h to FIG. Then, the phase housing 80 makes one rotation of 45 degrees × 8 times, which corresponds to the amount by which each of the air chambers A and B completes eight strokes.

That is, the operation from FIG. 77a to FIG.
Each of the air chambers A and B rotates 225 degrees, which corresponds to one stroke, and the phase housing 80 rotates 45 degrees. At this time, each air chamber A and B uses the housing flow passage holes 89 and 89 as an intermediary. Since both are joined to the separate housing flow passage holes 19 of the two streaks, as shown in FIGS.
The air chamber A joined to the rear half of n is the intake stroke,
As shown in (b) to (b) of FIG. B, the air chamber B joined to the front half of the exhaust hole Ex is the exhaust stroke. From there air chamber A,
When B is rotated by 225 degrees, the operation from the next figure b to the figure c is as follows.
It is an intake stroke from (a) to the intake hole In shown in FIG.

From the figure c, the air chambers A and B are further rotated by 225 degrees, and the operation up to the diagram d is such that there is no joint between the air chambers A and B and the housing flow passage holes 19 and 19. Is figure c
In (a), the expansion stroke in which the working medium is ignited and the compression stroke after the air chamber B is supplied are shown. Further, the air chambers A and B are rotated by 225 degrees, which corresponds to one stroke each, and the air chambers A and B are rotated from FIG.
The operation up to e is performed by the air chamber A from FIG.
As shown in e (b), the housing flow path hole 1 of the exhaust hole Ex
The exhaust stroke is completed by joining with 9 and the air chamber B is shown in FIG.
The expansion stroke of the working medium ignited at is ended. Then, the air chambers A and B, which have reached FIG. 78e, make two and a half rotations (225 degrees × 4) from FIG. 77a, and also the phase housing 80
Rotates half a turn (45 degrees × 4), during which each of the air chambers A and B makes four strokes to complete one cycle.

Then, as shown in FIGS. E to f, when the air chambers A and B are further rotated by 225 degrees and the phase housing 80 is rotated by 45 degrees in the same direction, the air chamber A is again in the intake stroke, The air chamber B performs the exhaust stroke, and further, from FIG. F to FIG.
In the operation for one stroke up to (b), the air chamber A is the compression stroke again, and the air chamber B is the intake stroke again. The operation from the next diagram g to h (a) and (b) is that the air chamber A is in the expansion stroke, the air chamber B is in the compression stroke again, and from FIG. When the phase housing 80 rotates by 45 degrees, the air chamber A ends the exhaust stroke and the air chamber B ends the expansion stroke again, and starts operation.
Return to. Eventually, both air chambers A and B perform 8 strokes in each cycle, and each air chamber A and B makes 5 revolutions (225 degrees x 8) to return the phase to the original state. The phase housing 80 following the rotation of the chambers A and B also makes one rotation in the same direction to restore the phase.

[0238] As shown in Figs. 77c (a) and 78g (a), at least two igniters Ig in the configuration of the forward rotation ratio of 5: 1 (5/1) are used for the air chamber A, and Fig. 77d.
As shown in (a) and FIG. 78h (a), at least two air chambers B are inserted on the same circumference of the wall of the housing 10 that can be ignited from the same ignition hole 86. Two of the chambers A face each other and two of the air chambers B also face each other, and the air chambers A and B are separated by 45 degrees corresponding to the rotation angle of one stroke in the phase housing 80. Also, this igniter Ig
Regarding the insertion and attachment of the phase housing 80 (the shaft plate 24 in each of the examples of modes 1 and 2, the phase plate 56 and the mode 5 in the examples of mode 4) in all the modes in which the forward rotation ratio of the primary rotation Po is high.
In the embodiment, the Z-axis housing 70) or the required number of the slanting plates 40 may be embedded in the slanting plate 40 or the like, but the ignition hole 86 is not necessary in that case.

7: 1 (7/1) in the form in which the forward rotation ratio of the primary rotation Po is high is 3: 1 (3/1),
Similar to the 5: 1 (5/1) configuration, an ignition hole (fuel injection hole) 86 is provided at a position where two housing flow path holes 89, 89 for the air chambers A and B face each other in the phase housing 80. Channel hole 89,
At the intermediate position of 89, the three members are drilled with different circumferences. The housing flow passage holes 19 formed in the wall of the housing 10 on the two housing flow passage holes 89, 89 have three streaks equally spaced on each circumference, each of which is approximately 1/6 of the circumference. Put
The three muscles of the two circumferences open at the same central angle where half the lengths of each other are overlapped, and the three muscles of one circumference are the intake holes (I
n × 3) and the other three lines on the circumference are exhaust holes (Ex
X3).

In this 7: 1 (7/1) configuration, the air chambers A and B make 7 rotations (210 degrees × 12) while the phase housing 80 makes one rotation, but the phase housing 80 is equivalent to 30 degrees. , Air chamber A,
Since the rotation of B by 210 degrees corresponds to one stroke, each of the air chambers A and B ends the operation of 12 strokes corresponding to three cycles for each rotation of the phase housing 80. In this case, the igniter Ig is installed in the same circumference of the wall of the housing 10 facing the ignition hole 86 at three equal intervals for three air chambers A and B for three cycles. Alternatively, the forward turn ratio is 9: 1 (9
In the case of / 1), the housing flow passage holes (In × 4, Ex × 4) are formed by four lines each having a circumferential length of about 1/8,
Air chamber A for one rotation (22.5 degrees × 16) of the phase housing 80,
B performs 9 rotations (202.5 degrees × 16) and operates in 16 strokes each for 4 cycles, and four ignition tools Ig are inserted and inserted for each of the air chambers A and B.

[0241]

[Form in which the forward rotation ratio of the secondary rotation is higher than that in the primary rotation] Next, the above-mentioned forms 1, 2, 3, 4, in which the secondary rotation Ne can set a forward rotation ratio higher than that in the primary rotation Po. In each of Examples 6 and 7, the forward ratio is 1: 3 (1/3) as an example.
In the embodiment of the sixth embodiment configured as described above, both half-moon shaped working chambers Ha, Ha
A description will be given based on FIG. 79 formed in the air chambers A, B, C and D of the minutes.

As shown in FIG. 79, a Z-axis gear 27, which is an external gear, is attached to the Z-axis 23-axis neck, and a casing gear 62 attached to a casing 60 is attached to the Z-axis gear 27 on the concentric circle of the Z-axis gear 27. Two intermediate gears 54, 5 are formed on the internal gear having a double pitch pitch diameter, and the Z-axis gear 27 and the housing gear 62 rotate with respect to each other by stereotactic rotation and mesh with each other.
4 is interposed, one of which is externally meshed with the Z-axis gear 27 and the other is internally meshed with the housing gear 62. When the Z-axis 23 is then rotated, the Z-axis gear 27 first rotates, and the Z-axis gear 27 rotates by rotating the two intermediate gears 54, 5
After the meshing of No. 4, the casing gear 62 is rotated in the same direction at the 1/3 speed of the Z axis 23.

That is, one rotation of the Z-axis 23 rotates the housing 60 one third in the same direction, but the rotary piston 30,
Also, the air chambers A, B, C and D are also rotated 1/3 to perform a forward rotation ratio of 1: 3 (1/3). In this case, one stroke in which the rotary piston 30 and the skewed plate 61 of the housing change the mutual plate surface gap to the maximum is performed every 270 degrees of rotation of the rotary piston 30 at the forward rotation ratio of 3: 1. However, at the forward rotation ratio of 1: 3, the rotation piston 30 is rotated by 90 degrees, and the Z axis 23 is rotated by 270 degrees during that time. Therefore, one rotation of the housing 60 and the rotation piston 30 and the Z axis is performed. Two
Three rotations of 3 changes the air gaps of the air chambers A, B, C, D corresponding to four strokes of intake, compression, expansion, and exhaust by 4 changes.

Although not shown, the working medium inflow / outflow holes In and Ex are the same as in the case of the embodiment 6 in the forward / reverse rotation described above, but the inner surface of the housing 60 or each plate of the housing slanting plate 61. The housing flow passage holes 69, 69, 69, 69, which are open to communicate with the outer surface of the housing 60 from both surfaces, and a groove-like shape penetrating from the inner wall surface of the housing 10 on the outer circumference of the outer surface hole opening to the outer wall surface The two holes of the housing flow passage holes 19 and 1 are the intake holes In on the advance side of the housing 60 rotation and the exhaust holes Ex on the delay side.
9 and are provided. In addition, each of the housing flow passage holes 69 that communicates with each of the air chambers A, B, C, and D separately shares the intake hole In and the exhaust hole Ex, and each of the outer surface hole openings thereof is The housing 60 is opened on the outer surface of the housing 60, which is evenly spaced by 90 degrees, on the same circumference of rotation, and the two housing flow passage holes 19 and 19 are provided.
Has a streak length of approximately ¼ of the circumference of the inner wall surface of the housing 10, and the inner wall surface side hole openings of the housing 10 are continuous in the same circumference and open. Further, the igniter Ig is inserted into the wall of the housing 10 (preferably one for each half-moon shaped operation chamber Ha) on the rotation circumference, which covers the outer surface hole opening of each housing flow path hole 69.

2 constructed as above and applied to the Z-axis 23
The rotation of 70 degrees causes the housing 60 to rotate by 90 degrees to change the air chamber gaps of the air chambers A, B, C, D to the maximum, and at that time, the respective housing flow passage holes 69 are changed to the housing flow passage holes. Since it rotates on the opening circumference of the inner side hole mouths of 19, 19, when the connection is synchronized with the increase and decrease of the air chambers A, B, C, D, the air chambers A, B, C corresponding to the air spaces. , D, either suction or exhaust hole In, Ex is opened to perform either suction or exhaust stroke, and if there is no connection, either compression or expansion stroke is performed. Even when the working medium is ignited by the igniter Ig fitted in the compression space, the ignition advance is synchronized so that the so-called piston is located at the top dead center when the maximum combustion pressure is at the highest compression stroke. To operate.

Further, as an example, the structure of the forward rotation ratio of 1: 3 (1/3) in the embodiment of the first embodiment will be described. Although not shown, the rolling gear 76 of the external gear mounted on the end of the rolling shaft 72 is used. On the other hand, the fixed phase gear 14 of the external gear having the 1/3 pitch circle diameter is fixed to the wall of the housing 10 on the Y axis so as to match the mounting plane of the rolling gear 76, and the rolling gear 76 is fixed phase gear. 14 is externally meshed. When the Z-axis 23 is then rotated, the rolling shaft 72 fitted on the connecting rod 26 also turns together with the connecting rod 26. This rolling shaft 72 is rotated by the rolling gear 76 externally meshed with the fixed phase gear 14. Z only in the direction of rotation of the Z axis 23
The same number of turns is made for one rotation of the shaft 23, and at the same time 1
/ Rotating for 3 rotations, 1/3 of the rotation of the rolling shaft 72
The rotation also causes the rotary piston 30 and the skew plate 40 to make 1/3 rotation to establish a forward rotation ratio of 1: 3 (1/3).

Next, the four strokes of one cycle at a forward rotation ratio of 1: 3 (1/3) configured and operated as described above,
As an example of the embodiments 6 and 7, the air chambers A, B, C, D
Based on FIG. 80 showing the existence of the above, description will be made for one rotation of the housing 60. In FIGS. 80a, 80b, 80c, 80c, 80d, 80c, 80d, 80d, 80c, 80d, 80a, 80b, 80c, 80d, 80a, 80b, 80c, 80d, 80a, 80b, 80c, 80d, 80a, 80b, 80c, and 100d, the reference numeral A indicates the housing chamber flow path 69 communicating with the air chamber. The air chambers B, C, D of the
The respective housing flow passage holes 69, 69, 69 communicating with D are shown.

First, in FIG. 80a, the air chamber A corresponds to the top dead center position of the piston where the housing flow passage hole A is out of the connection with the housing flow passage hole 19 on the exhaust hole Ex side, and the housing flow passage to be connected next is shown. The passage hole 19 is the intake hole In, and the air chamber B corresponds to the bottom dead center position of the piston where the housing passage hole B starts joining with the housing passage hole 19 on the exhaust hole Ex side. At this time, in the air chamber C, the housing flow passage hole C sucks, and there is no joint with the exhaust passages In and Ex, either of the housing flow passage holes 19, 19, and the closed working maximum compression medium is ignited at the top dead center. Position to,
The air chamber D is at a rotation angle position where the housing flow passage hole D is disengaged from the joint with the housing flow passage hole 19 for intake air and the air chamber space is closed. Therefore, immediately after the air chamber A in FIG. A starts the intake stroke, the air chamber B starts the exhaust stroke, the air chamber C starts the expansion stroke, and the air chamber D starts the compression stroke.

The rotary piston 30, the air chambers A, B, C and D, and the housing 60 in FIG. 80 rotate clockwise and operate in the order of FIGS. A to b, c and d. When the rotary piston 30 and the housing 60 in FIG. 1 rotate 90 degrees and the Z-axis 23 simultaneously rotates 270 degrees, the air chambers A, B, C, D and the housing flow passage holes A, B, C, D At the rotation angle position shown in FIG. B, the operation for one stroke is completed. In this figure b, the air chamber A finishes its connection with the intake hole In and undergoes a compression stroke, and the air chamber B begins to connect with the intake hole In at the same time as it disengages from the exhaust hole Ex and the intake stroke, and C finishes the expansion stroke and starts the exhaust stroke, and air chamber D starts the expansion stroke at the rotation angle position corresponding to the top dead center where the working medium is ignited.

Furthermore, from FIG. B, each air chamber A, B, C, D is 9
When 0 degree is rotated and Z axis 23 is rotated by 270 degrees,
The air chambers A, B, C, and D are operated one stroke at a time.
In this figure c, the air chamber A is at the bottom dead center position where the working medium in the air chamber space that has reached the top dead center is ignited, the air chamber B is at the bottom dead center position where the intake stroke is finished, and the air chamber C is at the top dead center position. Since the exhaust stroke is completed and the air chamber D corresponds to the position of the bottom dead center after the expansion stroke, the air chamber A is the expansion stroke, the air chamber B is the compression stroke,
The air chamber C starts the intake stroke and the air chamber D starts the exhaust stroke. Then, from FIG.
When the Z-axis 23 is rotated by 270 degrees by rotating the air chamber A by one degree, the air chambers A, B, C, D are operated by one stroke each in FIG. Exhaust hole E
The exhaust stroke is started by joining with x, the air chamber B corresponds to the top dead center position where the compressed air is ignited, the air chamber C starts the compression stroke, and the air chamber D joins with the intake hole In. This is the position where the intake stroke has started.

Further, in addition, each air chamber A, B, in FIG.
When C and D rotate 90 degrees and the Z-axis 23 rotates 270 degrees, the air chambers A, B, C and D are operated by one stroke each and the operation returns to the starting point a in FIG. This figure d to figure a
In the meantime, the air chamber A whose air chamber volume has been changed from the maximum to the minimum is joined to the exhaust hole Ex of the housing flow passage hole 19 to end the exhaust stroke, and the air chamber B is not operated by the casing flow passage hole B. The closed volume of the air chamber is changed from the minimum to the maximum in the opposite direction to the air chamber A to end the expansion stroke, and the air chamber C is ignited with the working medium having the maximum compression, and the air chamber D enters the compression stroke. The position.

After all, FIG. A goes through FIG.
Returning to each air chamber A, B, C, D, and the rotary piston 3
0 and the housing 60 make one rotation (90 degrees x 4 times), and the Z-axis 23 makes three rotations (270 degrees x 4 times) in the same direction, while each of the air chambers A, B, C, D Intake, compression, expansion,
And, the operation of each four strokes of exhaust is completed. Therefore, the expansion stroke in the configuration of this forward rotation ratio of 1: 3 (1/3) is
In one cycle returning to FIG. A through FIGS. A to d, air chamber C is performed in FIG. A, air chamber D is performed in FIG. B, air chamber A is performed in FIG. C, and air chamber B is performed in FIG. Therefore, the four air chambers A, B, C and D repeatedly generate torque.

When the operation mode of this forward rotation ratio is carried out in each of the above-mentioned Examples 1 to 4, Modes 6 and 7 are used.
In place of the casing flow passage holes 69 in the embodiment of FIG.
If 9, 49 and 49 are opened, the following constitution and operation are the same as in the case of the embodiments of the above-mentioned modes 6 and 7. Also,
At the forward rotation ratio of 1: 3 (1/3), the casing flow passage holes A and C are arranged on the same rotation circumference of the outer peripheral surface of the casing 60, and the casing flow passage holes B and D are also made into the casing flow passage holes A and C. Different from each other, they are opened in the same rotation circumference of the outer peripheral surface of the housing 60 at intervals of 180 degrees facing each other, and the housing 10 wall on the two opening rotation circumferences has approximately 1 of the circumference. / 4 housing channel holes (In, Ex) × 2 each having a circumference of 2
May be provided, and the housing flow path holes A and C, B and D
Even if the openings are separated from each other by 90 degrees, the combination of opening them in the same circumference may be the case flow path holes A, D and B, C, and also the case flow path holes A, B, C. , D may be configured such that the opening circles are opened in three circles in which one competes with each other, or each circle is opened in four circles in different circles.

As a next example, the progression of four strokes at a normal rotation ratio of 1: 5 (1/5) is configured for the half-moon-shaped working chamber Ha of the air chambers A and B in the embodiments of the above modes 6 and 7. Moreover, one rotation of the rotary piston 30 and the housing 60 will be briefly described below with reference to FIG. 81. This turnover ratio is 1: 5 (1/5)
The two housing flow path holes A and B in the above are opened on the same rotation circumference of the outer peripheral surface of the housing 60 separated by 135 degrees or 225 degrees from each other, and the housing flow path holes (19, 19) × Two
Is approximately 1 / along the circumference of the opening rotation of the housing flow passage holes A and B.
The housing 1 has two groove-shaped holes with 8 circumferences each.
Although passing through the opposite wall 0, the two lines are the intake holes In, In on the advance side and the exhaust holes Ex, Ex on the delay side with respect to the rotation direction of the rotary piston 30 and the housing 60. Also,
The igniter Ig has a housing flow passage holes A, B at an intermediate position of a portion where the housing flow passage hole (In, Ex) × 2 is not formed.
At least one piece is inserted into each of the opposing walls of the housing 10 for checking the hole opening.

Incidentally, in the continuous view of a to h of FIG.
The operation from each drawing to the next drawing is a rotation of 45 degrees in the rotation angle of the air chambers A and B and the rotary piston 30 or the housing 60, and the Z axis 23 moves in the same direction.
Since the rotation is for 25 degrees, the operation returning from FIG. A to FIGS. B to h to FIG.
1 rotation (45 degrees × 8) of the Z axis 23 and 5 rotations (2
25 degrees × 8), which corresponds to the amount that each of the air chambers A and B completes eight strokes.

The operation from FIG. 81a to FIG.
And air chamber B is 45 degrees, which is equivalent to one stroke each, and Z
Although the shaft 23 rotates by 225 degrees, both the housing flow passage holes A and B have one housing flow passage hole 19 or 1 of the two lines.
The air chamber A has an intake stroke and the air chamber B has an exhaust stroke. The operation from FIGS. B to c in which the air chambers A and B are rotated by 45 degrees from there is a compression stroke of the space in which the air chamber A is closed, and an intake stroke in which the air chamber B is joined to the intake hole In. The operation shown in FIGS. C to d has no joint between the air chambers A and B and the housing flow passage holes 19 and 19, and the air chamber A is ignited in FIG.
Advances the compression process.

Further, in the operation from FIG. D to FIG. E, the air chamber A joins with the exhaust hole Ex to end the exhaust stroke, and in the air chamber B, the working medium ignited in FIG.
Then, the air chambers A and B reaching the figure e make a half turn (45 degrees x 4) from the figure a and the Z axis 23 makes two and a half turns (225 degrees x 225 degrees).
4), during which each of the air chambers A and B makes four strokes to complete one cycle. And that figure e
As shown in FIG. F, the air chambers A and B are at 45 degrees and the Z-axis 23
Rotate 225 degrees in the same direction, during that time, the air chamber A again performs the intake stroke and the air chamber B performs the exhaust stroke, and the air chambers A and B are 45 degrees and the Z-axis 23 is 225 degrees. The air chamber A is the compression stroke again and the air chamber B is the intake stroke again in one stroke from the rotation of the degree to the rotation from FIG.

In addition, in the operation up to the next FIG. G and FIG. H, the air chamber A again undergoes the expansion stroke, the air chamber B again undergoes the compression stroke, and the air chamber A further goes to the next exhaust stroke, air chamber B. When the expansion stroke is completed again, the operation returns to the starting point a in FIG. Eventually, each of the air chambers A and B performed 8 strokes in two cycles, and as described above, the air chambers A and B made one rotation of 45 degrees × 8 times, and at the same time, the Z axis 23 also. Rotate 5 times in the same direction to restore the phase. In addition, the igniter Ig has a casing 60 (the shaft plate 24 in each of the embodiments of the first and second embodiments and the fourth embodiment in the fourth embodiment) in all of the forms in which the forward rotation ratio of the secondary rotation Ne is high in addition to the insertion of the wall of the housing 10 described above. In the embodiment, the phase plate 56) or the slanting plate 40 is embedded in a required number so as to be embedded, and the attachment is free.

Alternatively, in the case where the forward rotation ratio of the secondary rotation Ne is higher than the primary rotation Po of 1: 7 (1/7), each of the housing passage holes A and B or the casing passage holes C and D is obtained. Two of them are housing 60
Two enclosure flow passages A, B and C, D separated by 210 degrees at the central angle of 30 degrees and having the same circumference.
0 Open on the outer peripheral surface. The four housing channel holes A, B,
Housing channel holes (1
9,19) × 3 is approximately 1/1 of the circumference within the same circumference
Three pairs of two continuous lines of groove-shaped holes each having a two-circumferential length have an equal interval, and each of the three lines on the advance side with respect to the rotation direction of the housing 60 has intake holes In, In, In. And each of the three lines on the delay side are formed as exhaust holes Ex, Ex, Ex.

In the structure having the forward rotation ratio of 1: 7 (1/7), the rotary piston 30, the housing 60, the air chambers A, B,
The Z-axis 23 makes seven revolutions (210 degrees x
12) Yes, 30 degrees of this housing 60, 2 of Z axis 23
Since rotation for 10 degrees is for one stroke, each air chamber A, B,
For C and D, the operation of 12 strokes corresponding to 3 cycles is completed for each rotation of the housing 60. Igniter Ig at this time
Are inserted into the wall of the housing 10 between the housing flow path holes (In, Ex) × 3 at equal intervals.

When the forward rotation ratio is 1: 9 (1/9), four pairs of housing flow passage holes (In, Ex ) × 4 is drilled, and the housing 60 and each air chamber A, B, C, D makes one rotation (2
The Z axis 23 rotates 9 times (202.5
The air chambers A, B, C, and D perform 16 strokes for 4 cycles each, and the number of ignition tools Ig inserted and inserted is at least 4.

[0262]

In the conventional reciprocating piston engine, the structure thereof has a cylindrical cylinder, a piston, a connecting rod, a crankshaft, a valve, etc., and the number of parts is large and complicated, and the engine volume per unit output is large, and In its operation, the inertial mass of the reciprocating part causes obstacles to prevent high-speed rotation of the engine, lowering the output and fuel consumption performance, and the piston is supported only by fitting it on the inner wall surface of the cylinder to support the localization axis. However, the piston slams the cylinder wall at the time of reversal at the upper end of the vertical sliding, causing piston slap that causes vibration and noise. In addition, the attachment of the intake and exhaust mechanisms is limited to only the head of the cylinder, and the valve device is attached to form a narrowed portion in the inlet and outlet holes of the working medium that blocks the flow of the inlet and outlet air. Less and reduce exhaust efficiency. In addition, since the combustion temperature in the cylinder is high, abnormal combustion and generation of nitrogen oxides (NOx), which are difficult to purify, are large, and high cooling performance is required.

In contrast to such a conventional reciprocating piston engine, the spherical rotary piston engine of the present invention is based on the above-described structure and operation. The engine shaft is a Z-shaped Z from the crankshaft.
The center of the rotary piston 30 and the points Ka and Kb on both ends of the piston intermediate shaft 33 are regarded as bearing parts for joint connection by replacing the shaft 23, the housing shaft 71, or the rotary shaft 20 having a straight shaft shape. At the same time, it has a structural feature that all the movable bodies involved in pressure reception / pressurization are contained in the spherical body of the outer shell. That is, by adopting a basic structure of a spherical shape consisting of the maximum volume and the minimum surface area in the three-dimensional shape, the ratio of the stroke volume to the engine volume is extremely large, there is no crank mechanism, it is a double-ended piston, the standard It is extremely lightweight and compact because there are four air chambers corresponding to four cylinders in the sphere.

Further, by eliminating the crankshaft from the engine shaft and eliminating the inertial force of the reciprocating mass due to the reciprocating acceleration movement of the piston, the piston slap unlike the reciprocating piston engine is not generated, and the upper limit of the average piston speed is increased. As the engine is pushed up to widen the rotation range of the engine, it means high-speed rotation of the engine, so high output is achieved.
Since the specific output of S / l is increased, the fuel efficiency is inevitably improved. In addition, each of the main parts configured by the combination of the rotary piston 30, the oblique plate 40 (or the housing oblique plate 61) and the engine shaft is simple, and the number of parts is small and the same parts are small at the same time. It is easy and clear and is not complicated, so it is advantageous for workability such as disassembly, assembly, maintenance, etc., and the spherical engine body is robust against thermal deformation, stress, impact load, and has high manufacturing accuracy from the mechanism. Since it does not require high assembly precision, it is low in cost, hard to break down, and highly durable.

In the comb-shaped working chamber Fu having a flat space formed in a spherical shape, the ratio of the area to the volume is remarkably large as compared with the conventional engine, and the working chamber space moves within the spherical concave surface. As a result, turbulence and agitation occur in the inflowing air, which promotes flame propagation and promotes complete combustion, and suppresses the generation of harmful CO due to incomplete combustion and the emission of unburned HC gas, resulting in high combustion. Efficiency is obtained. On the other hand, since the surface area of the combustion chamber wall that the flame contacts is large, the flame is cooled by the combustion chamber wall and the maximum combustion temperature is suppressed to a low level, and nitrogen oxide (NOx) of harmful exhaust gas generated at high temperature is generated. In addition to being hard to be knocked, there is little occurrence of abnormal combustion due to high temperature such as knocking or pinking.

In addition, such a low combustion temperature means that it is possible to manufacture an engine using an inexpensive material that is a low-grade material from the viewpoint of heat resistance, and requires a larger cooling device for high temperatures. In the combustion chamber that moves with combustion in the sphere, especially with combustion, the combustion heat is conducted and diffused to the wall of the combustion chamber to make the temperature of the entire engine uniform, and the rigidity of the engine due to the temperature difference
Reduces strength and suppresses bimetallic thermal deformation. Alternatively, the rotation outer peripheral surface of the rotating body and the inner surface of the working chamber forming a spherical surface are in surface contact which is particularly advantageous for generating a lubricating oil film and maintaining airtightness, and a plurality of working chambers share the same airtight tool. Therefore, it is also superior in handling, manufacturing and durability. Furthermore, the rotating load of the rotating body composed of a circular body is dispersed on the circular contact surface, which is advantageous for wear resistance, and the deformation of the working chamber due to the frictional resistance of reciprocating motion and the generation of leakage due to frictional wear. There are no elements.

It should be noted that the rotating body capable of rotating in the spherical surface enables symmetrical shaping, and the axisymmetric rotating body has a small moment of inertia and excellent transient characteristics, and has a good mechanical efficiency for vibrating rotationally. Low noise generation. On the other hand, sucking,
The exhaust mechanism does not have a valve installed, and unlike the conventional engine, it sucks in one place of the cylinder head, the exhaust holes do not concentrate, there is a degree of freedom in the hole diameter range of the intake and exhaust holes, and the mutual volume Since the two comb-shaped working chambers Fu and Fu which are inversely changed to form a pair continuously perform the intake stroke and the exhaust stroke, the inertial resistance mass of the air inflow and outflow is small, and the suction efficiency is excellent, and more A high average effective pressure value can be obtained because the intake air weight is taken.

As described above, according to the present invention, the structure and operation mode based on the principle of rotating piston, which is completely different from the conventional reciprocating piston engine, is shown. It was possible to realize small size, light weight and high rotation, and to suppress the generation of vibration and noise. Also, in the combustion state,
Complete combustion and low maximum temperature combustion can be obtained from the shape of the combustion chamber and the combustion chamber that moves on a spherical surface, and the low combustion temperature significantly reduces the generation of nitrogen oxides (NOx) which are harmful exhaust gases. Is. On the other hand, the combustion chamber concentrated in the sphere has many advantages such as suppressing the necessary heat dispersion and achieving a high level of thermal efficiency, and does not require a large cooling device. It is a high-performance rotary piston engine that achieves both power output and fuel efficiency that were contradictory and impossible to solve.

That is, the spherical rotary piston engine of the present invention has a high output and excellent fuel economy, produces little harmful exhaust gas, has no difficulty in parts and composition, is simple, plain, and easy to handle. Therefore, the manufacturing cost is significantly low and the cost is low. In addition, it is a durable product, lightweight and compact, and has many excellent effects such as being a quiet engine.

[Brief description of drawings]

FIG. 1 shows the principle of the present invention (solving means 1, 2, 3, 5, 6,
7 is a partial vertical perspective view of a basic figure showing 7). FIG.

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

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

FIG. 4 is a perspective view showing an angle change of a reference figure.

FIG. 5 is a perspective view showing an angle change of a reference figure.

FIG. 6 is a perspective view showing an angle change of a reference figure.

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

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

FIG. 9 is a perspective view showing an angle change of a reference figure.

FIG. 10 is a perspective view showing an angle change of a reference figure.

FIG. 11 is a perspective view showing a change in angle of a reference figure.

FIG. 12 is a perspective view showing a change in angle of a reference figure.

FIG. 13 is a perspective view showing a change in angle of a reference figure.

FIG. 14 is a perspective view of (a), (b), (c), (d), (e), and (f) showing the primary rotation in the solving means 1, 2, 3, 5, 6, 7.

FIG. 15 is a continuation of FIG. 14, and solving means 1, 2, 3, 5,
Shows primary rotation at 6 and 7 (G) (H) (L)
(Nu) (lu) (wo) perspective views.

16] The present invention (Solution means 1, 2, 3, 5, 6, 7)
(A) (B) (C) showing the operation of and the volume change of each air chamber
(D) (E) (F) partial longitudinal cross-sectional side view.

FIG. 17 is a continuation of FIG. 16 and the present invention (solving means 1, 2,
3, 5, 6, 7) operation and partial side views of (G), (H), (I), (J), (K), and (L) showing changes in volume of each air chamber.

FIG. 18 is a partial vertical perspective view of a basic figure showing the principle (solving means 4, 8) of the present invention.

FIG. 19 is a perspective view showing an angle change of a basic figure.

FIG. 20 is a perspective view showing a change in angle of a basic figure.

FIG. 21 is a perspective view showing an angle change of a basic figure.

FIG. 22 is a perspective view showing a change in angle of a basic figure.

FIG. 23 is a perspective view showing a change in angle of a basic figure.

FIG. 24 is a perspective view showing an angle change of a basic figure.

FIG. 25 is a perspective view showing a change in angle of a basic figure.

FIG. 26 is a perspective view showing a change in angle of a basic figure.

FIG. 27 is a perspective view showing a change in angle of a basic figure.

FIG. 28 is a perspective view showing an angle change of a basic figure.

FIG. 29 is a perspective view showing an angle change of a basic figure.

FIG. 30 is a perspective view showing an angle change of a basic figure.

FIG. 31 is a perspective view of (a), (b), (c), (d), (e), and (f) showing the primary rotation in the solving means 4 and 8.

32 is a perspective view of (g), (h), (g), (g), (g), (g), and (g) showing the primary rotation in the solving means 4, 8 following FIG. 31;

FIG. 33 shows the operation of the present invention (solving means 4, 8) and the volume change of each air chamber (A) (B) (C) (D) (E) (F).
Partial vertical section of each.

FIG. 34 is a sequel to FIG. 33, showing the operation of the present invention (solving means 4, 8) and the volume change of each air chamber (G) (H) (I).
(J) (K) (L) partial longitudinal cross-sectional side view.

FIG. 35 is a partially longitudinal side view showing the embodiment (1) of the first embodiment of the present invention (the numbers in parentheses indicate other solving means 1 to 1).
3).

FIG. 36 is an exploded perspective view of a partial cross section of FIG. 35.

FIG. 37 is a partial vertical cross-sectional side view showing an embodiment (2) of mode 1 of the present invention.

38 is a partially longitudinal side view showing the embodiment (3) of the form 1 in accordance with the present invention. FIG.

FIG. 39 is a partially longitudinal side view showing the embodiment (1) of the second aspect of the present invention.

FIG. 40 is a partially longitudinal side view showing an embodiment (2) of mode 2 of the present invention.

FIG. 41 is a partially longitudinal side view showing the embodiment (3) of the second aspect of the present invention.

FIG. 42 is another mode of the embodiment of form 2 (forward / reverse rotation ratio 1:
3) A partial vertical side view showing 3).

43] Another aspect of the embodiment of form 2 (forward / reverse rotation ratio 1:
3) A partial vertical side view showing 3).

FIG. 44 is a partial vertical cross-sectional side view showing the embodiment (1) of the form 3 in the present invention.

45 is an exploded perspective view, partly in section, of FIG. 44.

FIG. 46 is a partial vertical cross-sectional side view showing the embodiment (2) of the third embodiment of the present invention.

FIG. 47 is a partially longitudinal side view showing an example (3) of the form 3 in the present invention.

FIG. 48 is a partially longitudinal side view showing another mode (forward / reverse rotation ratio 1: 3) of the example (1) of the third embodiment.

FIG. 49 is a partial vertical cross-sectional side view showing the embodiment (1) of mode 4 in the present invention.

50 is an exploded perspective view, partly in section, of FIG. 49. FIG.

FIG. 51 is a partially longitudinal side view showing an example (2) of mode 4 of the present invention.

52 is a partial vertical cross-sectional side view showing the embodiment (3) of the form 4 in the present invention. FIG.

FIG. 53 is a partially longitudinal side view showing the embodiment (1) of the fifth aspect of the present invention.

FIG. 54 is a partially longitudinal side view showing an embodiment (2) of mode 5 of the present invention.

FIG. 55 is a partial vertical cross-sectional side view showing the embodiment (3) of the fifth aspect of the present invention.

FIG. 56 is a partially longitudinal side view showing the embodiment (1) of mode 6 of the present invention.

FIG. 57 is a partially longitudinal side view showing embodiment (2) of mode 6 of the present invention.

FIG. 58 is a partial vertical cross-sectional side view showing the embodiment (3) of mode 6 of the present invention.

FIG. 59 is a partially longitudinal side view showing the embodiment (1) of the seventh aspect of the present invention.

FIG. 60 is a partial vertical cross-sectional side view showing an embodiment (2) of mode 7 of the present invention.

FIG. 61 is a partially longitudinal side view showing an example (3) of the seventh aspect of the present invention.

FIG. 62 is a partial vertical cross-sectional side view showing the embodiment (1) of mode 8 of the present invention.

FIG. 63 is a partial vertical cross-sectional side view showing an embodiment (2) of mode 8 in the present invention.

FIG. 64 is a partial vertical cross-sectional side view showing an embodiment (3) of mode 8 of the present invention.

[FIG. 65] Forms 1, 2, 3, 5, 6, 7 according to the present invention
4 steps of (a) (b) (c) (d) (e) (f) (f)
FIG.

66 is a continuation of FIG. 65, modes 1, 2 in the present invention,
Show 4 steps of 3, 5, 6, 7 (G) (G) (G)
(Nu) (ru) (wo) Partial vertical side view.

FIG. 67 is a partial vertical sectional side view of (a), (b), (c), (d), (e), and (f) showing four strokes of modes 4 and 8 in the present invention.

FIG. 68 is a partial vertical cross-sectional side view of (G), (H), (G), (G), (G), and (W) showing four strokes of modes 4 and 8 in the present invention, subsequent to FIG. 67;

69] This invention (Solution means 1, 2, 3, 5, 6, 7)
6 is a partial vertical sectional front view showing the principle of torque generation in FIG.

FIG. 70 is a partial vertical sectional front view showing the principle of torque generation in the present invention (Solutions 4, 8).

71 shows four strokes (forward / reverse rotation ratio 1: 1) in another mode (intake / exhaust mechanism) of modes 1, 2, 4, 5, 8 a,
b, c, d each (i) (b) each partial longitudinal front view.

72 is a diagram showing four strokes (forward / reverse rotation ratio 3: 1) in another mode (intake / exhaust mechanism) of modes 1, 2, 4, 5, 8;
b, c, d each (i) (b) each partial longitudinal front view.

FIG. 73 is a continuation of FIG. 72 and is a four-stroke process (forward / reverse rotation ratio 3: in another mode (intake / exhaust mechanism) of modes 1, 2, 4, 5 and 8;
FIG. 2 is a partial vertical sectional front view of (a) and (b) of e, f, g, and h showing 1).

FIG. 74 is a form of forward rotation according to the present invention (forward rotation ratio 3:
1 is a partially longitudinal side view showing Embodiment 8) of FIG.

FIG. 75 is a form of forward rotation according to the present invention (forward rotation ratio 3:
1 is a partial vertical cross-sectional side view showing Embodiment 1) of FIG.

FIG. 76 shows the forward turn ratios in forms 1, 2, 4, 5, and 8:
The partial longitudinal front view of each of (a) and (b) of a, b, c, d showing the four strokes of 1.

77 is a ratio of forward turn 5 in forms 1, 2, 4, 5, and 8:
The partial longitudinal front view of each of (a) and (b) of a, b, c, d showing the four strokes of 1.

78 is a continuation of FIG. 77, and each part (a) and (b) of e, f, g, and h showing four strokes in the forward ratio of 5: 1 in the forms 1, 2, 4, 5, and 8. FIG.

FIG. 79 shows a form of forward rotation in the present invention (forward rotation ratio 1:
3 is a partially longitudinal side view showing the third embodiment 6).

80 is a partial vertical sectional front view showing a, b, c, and d showing four strokes in the forward rotation ratio 1: 3 in the forms 1, 2, 3, 4, 6, and 7. FIG.

81 is a, b, c, d, e, f, g, h showing four strokes in the forward ratio 1: 5 in the forms 1, 2, 3, 4, 6, 7. FIG.
FIG.

[Explanation of symbols]

G spherical surface O spherical center of spherical surface G radius of spherical surface G X X axis line (main axis of rotation, rolling axis, rotation axis of pivot) Y Y axis line (formation axis of S circle surface, rotation axis of skew plate) θ θ angle (An intersecting angle of the X axis and the Y axis on the acute angle side) P P point (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 Diameter of bottom surface, conical locus of apex with spherical center O) J Conical locus J (radius of bottom surface with points P and Q, conical locus of apex with spherical center O) M M axis (vertical axis of X axis and R circle, Pin joint joint joint axis) R R circle surface (horizontal circle surface on X axis line) S S circle surface (vertical circle surface of Y axis line) L L axis line (rotation axis line of R circle surface) K K axis line (R circle) (Intersecting secant of plane and S circle, vertical line of M axis) Ka K One end point of K axis Kb One end point of K axis One end point Ha Half-moon space, half-moon operation Chamber Fu Comb-shaped space, Comb-shaped working chamber In Intake hole Ex Exhaust hole Ig Ignition device or fuel injection valve A Space A, Air chamber A, Comb-shaped working chamber A, Case flow path hole A
(Modes 6 and 7) B space B, air chamber B, comb-shaped working chamber B, casing flow path hole B
(Modes 6 and 7) C Space C, air chamber C, comb-shaped working chamber C, housing flow path hole C
(Modes 6 and 7) D Space D, air chamber D, comb-shaped working chamber D, housing flow path hole D
(Modes 6 and 7) Po Primary rotation Ne Secondary rotation 10 Housing 11 Housing concave surface inner wall 12 Orbital gap 13 Main bearing 14 Fixed phase gear 15 Shaft plate chamber 19 Housing passage hole 20 Rotating main shaft 21 Rotating main shaft shaft center 22 Main shaft Gear 23 Z-axis 24 Shaft plate 25 Shaft arm 26 Connecting rod 27 Z-axis gear 28 Gear pocket 29 Shaft plate passage hole 30 Rotating piston 31 Rotating piston arcuate surface 32 Rotating piston spherical arc surface 33 Piston intermediate shaft 34 Piston shaft Hole 35 Piston pivot 40 Oblique plate 41 Oblique plate and arcuate surface of oblique plate of housing 42 Oblique plate and chord side surface of oblique plate of housing 43 Oblique plate ring 44 Oblique plate ring gear 45 Outer sliding Contact surface 49 Oblique plate flow path hole 50 Hinge joint 51 Hinge pin 52 Hinge pin receiver 54 Intermediate gear 55 Pin joint joint 56 Phase plate 57 Phase plate bearing 58 Phase plate gear 59 Phase plate flow path hole 60 Body 61 Case skew plate 62 Case case gear 63 Case case bearing 64 Case shaft plate chamber 69 Case case passage hole 70 Z axis case 71 Case axis 72 Rolling shaft 73 Rolling bearing 74 Central axis 76 Gear 80 phase housing 81 concave inner wall of phase housing 82 phase housing housing gear 83 phase housing housing bearing 86 ignition hole or fuel injection hole 87 Z axis housing, phase housing orbital gap 88 pivots 89 Z axis housing, phase housing Case flow path

─────────────────────────────────────────────────── ─── Continuation of front page (58) Fields surveyed (Int.Cl. ⁷ , DB name) F01C 3/06 F01C 9/00 F02B 53/00

Claims (11)

(57) [Claims] 1. A straight line intersecting at a spherical center (O) having a spherical surface (G) having a radius (r) with the spherical center (O) as the center of the housing (10) and having an angle (θ). The axis (X) is the axis (Y), the point where the axis (X) intersects the spherical surface (G) is the point (P), and the point where the axis (Y) intersects the spherical surface (G) is the point (Q). P) The conical locus with the diameter of the bottom surface between the points (Q) and the apex of the spherical center (O) is defined as the conical locus (U), and the distance between the points (P) and (Q) is half the diameter of the bottom surface. A conical locus having (O) as an apex is a conical locus (J), an axis line orthogonal to the axis line (X) at the spherical center (O) is an axis line (M), and a horizontal plane is formed on the axis line (X). The great circle plane in the spherical surface (G) having the axis (L) of the diameter line segment as the axis of rotation is the circular surface (R) and the axis (Y)
Is a vertical axis and a great circle plane formed through a spherical center (O) in a spherical surface (G) is a circular surface (S), and the circular surface (R) and the circular surface (S) are spherical centers (O). Intersect at and axis (M)
The axis (K) is defined as the intersecting secant forming the perpendicular line of the housing, and both ends of the intersecting secant (K) are defined as points (Ka) and points (Kb).
In (0), each of the raceway gaps (12) formed in the groove surrounding the inner wall portion of the housing (10) along the extension plane of the circular surface (S) and the opposing both walls on the axis (Y) are circular. A shaft plate chamber (15), which is formed by notching in the recess, is provided outside the spherical surface (G), and a main bearing (1) is provided at the center of the side wall of each shaft plate chamber (15).
3) through which the shaft plates (24) rotatably housed in the shaft plate chambers (15) are provided in both main bearings (13) of the shaft lines (X).
The Z-axis (2
3) A pin joint joint in which both shaft necks are supported, a tubular rolling shaft (72) is externally fitted to the connecting rod (26), and an axis (M) serves as a connecting shaft at the central portion of the rolling shaft (72). (5
5) has an axial center (74) consisting of a circular body, and on the circular surface (R), there is a spherical arc surface (32) of the outer peripheral surface which is in sliding contact with the spherical surface (G) and the spherical arc surface (32). An arcuate contour plane, a bow surface (31) having a chord on the axis (K) side, and a cylindrical piston intermediate shaft (33) joined to the chord side of the bow surface (31). A plate-shaped rotary piston (30) is arranged so that the rolling shaft (72) is inserted therethrough, and a piston pivot (35) for receiving the circular body of the axial center (74) is provided in the inner center of the rotary piston (30). The piston pivot (35) is pivotally attached to the pivot (74) about the axis (X) so that the piston pivot (35) can pivot within a range of angle (θ) × 2 and the piston intermediate shaft. (33) A pin of a hinge joint (50) whose joint base axis is the intersection secant (K) on the side of the points (Ka) and (Kb) at both ends. Or consisting of a pin receiving hole provided one of the connecting elements, also arcuate surface on the circular surface (S) (41) and its arcuate surface (4
A circular plate shape having an arcuate slant plate ring (43) formed on the outer periphery, which has the arcuate contour surface and the chordal side surface (42) of 1) and has an inner peripheral surface side fixedly attached to the arcuate contour surface. Skew board (4
0) is arranged so that the slanting plate ring (43) is rotatably fitted in the orbital space (12), and is facing at the point (Ka) point (Kb) of the slanting plate ring (43). When a connecting element corresponding to the connecting element of the hinge joint (50) is provided and fitted to the portion, the oblique plate (40) and the rotary piston (30) form an angle with the intersecting secant (K) as the hinge axis. (Θ) × 2 range is slidably connected, and the peripheral wall of the shaft plate chamber (15) is engraved on the fixed phase gear (14) of the fixed gear and the end of the rolling shaft (72) of the external gear is formed. A rolling gear (76) is provided to provide a fixed phase gear (1
4) meshed with each other, and then the slanting plate (40) on the circular surface (S) was attached to the housing (1
0), the inner concave surface forming the spherical surface (G) is closed to form a half-moon-shaped working chamber (Ha) in a hemispherical space, and the half-moon-shaped working chamber (Ha) is formed on the circular surface (R) by a rotary piston (30). ) Is formed in a comb-shaped working chamber (Fu) that forms a comb-shaped space, and is further exposed to the comb-shaped working chamber (Fu).
n) and an exhaust hole (Ex) are provided, and a igniter (Ig) or a fuel injection valve is inserted and attached by checking the combustion chamber, and a spherical rotary piston engine. 2. Each of two straight lines intersecting at a spherical center (O) having a spherical surface (G) having a radius (r) with the spherical center (O) as the center of the housing (10) and having no angle (θ). The axis (X) is the axis (Y), the point where the axis (X) intersects the spherical surface (G) is the point (P), and the point where the axis (Y) intersects the spherical surface (G) is the point (Q). P) The conical locus with the diameter of the bottom surface between the points (Q) and the apex of the spherical center (O) is defined as the conical locus (U), and the distance between the points (P) and (Q) is half the diameter of the bottom surface. A conical locus having (O) as an apex is a conical locus (J), an axis line orthogonal to the axis line (X) at the spherical center (O) is an axis line (M), and a horizontal plane is formed on the axis line (X). The great circle plane in the spherical surface (G) having the axis (L) of the diameter line segment as the axis of rotation is the circular surface (R) and the axis (Y)
Is a vertical axis and a great circle plane formed through a spherical center (O) in a spherical surface (G) is a circular surface (S), and the circular surface (R) and the circular surface (S) are spherical centers (O). Intersect at and axis (M)
The axis (K) is defined as the intersecting secant forming the perpendicular line of the housing, and both ends of the intersecting secant (K) are defined as points (Ka) and points (Kb).
In (0), each of the raceway gaps (12) formed in the groove surrounding the inner wall portion of the housing (10) along the extension plane of the circular surface (S) and the opposing both walls on the axis (Y) are circular. A shaft plate chamber (15), which is formed by notching in the recess, is provided outside the spherical surface (G), and a main bearing (1) is provided at the center of the side wall of each shaft plate chamber (15).
3) penetrating through each of the main bearings (13), each of the shaft plates (24) rotatably fitted in each of the shaft plate chambers (15) is connected to the connecting rod (26) on the axis (X). Z-axis (23) connecting to form a Z-shape
A circular body element of a pin joint joint (55) having a shaft (M) as a connecting shaft at the central portion of a connecting rod (26) positioned at the spherical center (O) of the Z-axis (23) by supporting both of the shaft necks. And a spherical arc surface (32) of the outer peripheral surface which is in sliding contact with the spherical surface (G) on the circular surface (R) and an arcuate contour plane of the spherical arc surface (32). A substantially plate-shaped rotary piston (30) having an arcuate surface (31) having a chord on the axis (K) side, and incorporating a cylindrical piston intermediate shaft (33) on the chord side of the arcuate surface (31). ) Is inserted through the connecting rod (26) of the Z-axis (23), and a piston pivot (35) for receiving the circular body element of the pivot connector (88) is formed in the inner center of the rotary piston (30). The piston pivot (35) is connected to the pivot connector (88), and the connecting rod (26) on the axis (X) is used as the base axis (angle (θ) ×).
Of the piston intermediate shaft (3
3) A connecting element composed of a pin or a pin receiving hole of a hinge joint (50) whose joint base axis is the intersection secant (K) is provided on both sides of the points (Ka) and (Kb) at both ends, and the circular surface (S) ) Above it is an arched surface (41) and its arched surface (4
A circular plate shape having an arcuate slant plate ring (43) formed on the outer periphery, which has the arcuate contour surface and the chordal side surface (42) of 1) and has an inner peripheral surface side fixedly attached to the arcuate contour surface. Skew board (4
0) is arranged so that the slanting plate ring (43) is rotatably fitted in the orbital space (12), and is facing at the point (Ka) point (Kb) of the slanting plate ring (43). When a connecting element corresponding to the connecting element of the hinge joint (50) is provided and fitted to the portion, the oblique plate (40) and the rotary piston (30) form an angle with the intersecting secant (K) as the hinge axis. (Θ) × 2 range is slidably connected, and the Z-axis gear (2) of the external gear is attached to the Z-axis (23) axis neck.
7) is attached and the circumference of the edge portion of the slanting plate ring (43) is also engraved on the slanting plate ring gear (44), and the intermediate gear (5
4) is interposed, and the slanting plate (40) on the circular surface (S) is then attached to the housing (1).
0), the inner concave surface forming the spherical surface (G) is closed to form a half-moon-shaped working chamber (Ha) in a hemispherical space, and the half-moon-shaped working chamber (Ha) is formed on the circular surface (R) by a rotary piston (30). ) Is formed in a comb-shaped working chamber (Fu) that forms a comb-shaped space, and is further exposed to the comb-shaped working chamber (Fu).
n) and an exhaust hole (Ex) are provided, and a igniter (Ig) or a fuel injection valve is inserted and attached by checking the combustion chamber, and a spherical rotary piston engine. 3. Two straight lines intersecting each other at a spherical center (O) having a spherical surface (G) having a radius (r) with the spherical center (O) as the center of the housing (10) and forming an angle (θ). The axis (X) is the axis (Y), the point where the axis (X) intersects the spherical surface (G) is the point (P), and the point where the axis (Y) intersects the spherical surface (G) is the point (Q). P) The conical locus with the diameter of the bottom surface between the points (Q) and the apex of the spherical center (O) is defined as the conical locus (U), and the distance between the points (P) and (Q) is half the diameter of the bottom surface. A conical locus having (O) as an apex is a conical locus (J), an axis line orthogonal to the axis line (X) at the spherical center (O) is an axis line (M), and a horizontal plane is formed on the axis line (X). The great circle plane in the spherical surface (G) having the axis (L) of the diameter line segment as the axis of rotation is the circular surface (R) and the axis (Y)
Is a vertical axis and a great circle plane formed through a spherical center (O) in a spherical surface (G) is a circular surface (S), and the circular surface (R) and the circular surface (S) are spherical centers (O). Intersect at and axis (M)
The axis (K) is defined as the intersecting secant forming the perpendicular line of the housing, and both ends of the intersecting secant (K) are defined as points (Ka) and points (Kb).
In (0), the inner wall surface of the housing (10) is formed as the inner wall surface forming the spherical surface (G), and the orbital gap (12) of the groove that surrounds the inner wall portion along the extension plane of the circular surface (S). And a main bearing (13) is pierced on both opposing walls on the axis (Y). The main bearing (13) has a shaft arm (2) having an arbitrary shape.
Each of 5) is connected to the connecting rod (26) on the axis (X) to support the Z-shaped neck of the Z axis (23) and is positioned at the spherical center (O) of the Z axis (23). A pin joint joint (55) having an axis (M) as a connecting axis at the center of the connecting rod (26)
A pivot connector (88) consisting of a circular body element is attached, and a spherical arc surface (32) of an outer peripheral surface slidingly contacting a spherical surface (G) on the circular surface (R) and an arcuate contour plane of the spherical arc surface (32). And an arcuate surface (31) having the axis (K) side as a chord, and a cylindrical piston intermediate shaft (33) united to the chord side of the arcuate surface (31). A rotary piston (30) is arranged by inserting an intermediate portion of the Z-axis (23) between the shaft arm (25) and the connecting rod (26).
0) has a piston pivot (35) for receiving the circular body element of the pivot connector (88) formed in the inner center of the piston pivot (3).
5) Connect the pivot rod (88) to the connecting rod (26) on the axis (X).
Is pivotally mounted in a range of angle (θ) × 2 with respect to the base axis and the intersection secant (K) is the joint base axis on the side of the points (Ka) and (Kb) at both ends of the piston intermediate shaft (33). A connecting element consisting of a pin or a pin receiving hole of the hinge joint (50) is provided, and an arcuate surface (41) and its arcuate surface (4) are provided on the circular surface (S).
A circular plate shape having an arcuate slant plate ring (43) formed on the outer periphery, which has the arcuate contour surface and the chordal side surface (42) of 1) and has an inner peripheral surface side fixedly attached to the arcuate contour surface. Skew board (4
0) is arranged so that the slanting plate ring (43) is rotatably fitted in the orbital space (12), and is facing at the point (Ka) point (Kb) of the slanting plate ring (43). When a connecting element corresponding to the connecting element of the hinge joint (50) is provided and fitted to the portion, the oblique plate (40) and the rotary piston (30) form an angle with the intersecting secant (K) as the hinge axis. (Θ) × 2 range is slidably connected, and the Z-axis gear (2) of the external gear is attached to the Z-axis (23) axis neck.
7) is attached and the circumference of the edge portion of the slanting plate ring (43) is also engraved on the slanting plate ring gear (44), and the intermediate gear (5
4) is interposed, and then the slanting plate (40) on the circular surface (S) closes the concave inner wall (11) of the housing (10) forming the spherical surface (G) to form a half-moon-shaped working chamber (). Ha) and the half-moon shaped working chamber (Ha) is formed into a comb-shaped working chamber (Fu) in which a rotary piston (30) on a circular surface (R) forms a comb-shaped space, and the comb-shaped working chamber is further formed. (Fu) facing the suction hole (I
n) and an exhaust hole (Ex) are provided, and a igniter (Ig) or a fuel injection valve is inserted and attached by checking the combustion chamber, and a spherical rotary piston engine. 4. A straight line intersecting at a spherical center (O) having a spherical surface (G) having a radius (r) with the spherical center (O) as the center of the housing (10) and having an angle (θ). The axis (X) is the axis (Y), the point where the axis (X) intersects the spherical surface (G) is the point (P), and the point where the axis (Y) intersects the spherical surface (G) is the point (Q). P) The conical locus with the diameter of the bottom surface between the points (Q) and the apex of the spherical center (O) is defined as the conical locus (U), and the distance between the points (P) and (Q) is half the diameter of the bottom surface. A conical locus having (O) as an apex is a conical locus (J), an axis line orthogonal to the axis line (X) at the spherical center (O) is an axis line (M), and a horizontal plane is formed on the axis line (X). The great circle plane in the spherical surface (G) having the axis (L) of the diameter line segment as the axis of rotation is the circular surface (R) and the axis (Y)
Is a vertical axis and a great circle plane formed through a spherical center (O) in a spherical surface (G) is a circular surface (S), and the circular surface (R) and the circular surface (S) are spherical centers (O). Intersect at and axis (M)
The axis (K) is defined as the intersecting secant forming the perpendicular line of the housing, and both ends of the intersecting secant (K) are defined as points (Ka) and points (Kb).
0), the inner wall surface of the housing (10) is formed into a spherical surface (G) larger than the concentric spherical surface (G), and the main bearing (1) is provided on the opposing wall of the housing (10) on the axis (X).
3) is penetrated, and both main bearings (13) have a rotary main shaft (2
No. 0) bearing both side shaft necks, and a central shaft center consisting of a circular body of a pin joint joint (55) having an axis (M) as a connecting axis at a central portion located at a spherical center (O) of the rotating main shaft (20). (21)
On the circular surface (R), the spherical arc surface (32) of the outer peripheral surface which is in sliding contact with the spherical surface (G) and the arcuate contour plane of the spherical arc surface (32) are formed so that the axis (K) side is A substantially plate-shaped rotary piston (30) having an arcuate surface (31) as a chord and having a cylindrical piston intermediate shaft (33) joined to the chord side of the arcuate surface (31) is the rotary spindle (30). 20) is loosely inserted and a piston center (35) for receiving the circular body of the shaft center (21) is formed in the inner center of the rotary piston (30), and the piston center (35) is centered. The rotation main shaft (20) on the axis (X) is pivotally attached to (21) so as to be swingable in a range of angle (θ) × 2, and the points (Ka) ((Ka)) at both ends of the piston intermediate shaft (33) ( On the Kb) side, a connecting element consisting of a pin or a pin receiving hole of a hinge joint (50) with the intersection secant (K) as the base axis of the joint. And has an arcuate surface (41), an arcuate contour surface of the arcuate surface (41) and a chord side surface (42) on the circular surface (S), and the inner peripheral surface side is integrally formed with the arcuate contour surface. A circular plate-shaped skew plate (40) having an annular skew plate ring (43) formed on the outer periphery, which is coupled and rotatably engages with the inner wall surface of the housing (10), is arranged. ) Point (Ka) point (K
When a connecting element corresponding to the connecting element of the hinge joint (50) is provided and fitted in the opposing portion located in b), the oblique plate (40) and the rotary piston (30) connect the intersecting secant (K). A phase plate (56) which is a concave plate having an angle (θ) × 2 range slidably connected as an axis of hinge attachment and having an inner surface of a spherical surface (G) on each side sandwiching the slant plate ring (43). Is installed and a phase plate bearing (57) penetrating above the point (P) is provided in each of the phase plates (56), and the rotary spindle (20) is fitted and inserted, and the phase is formed on the outer surface of the upper phase plate (56). The phase plate gear (58) of the external bevel gear is attached around the hole of the plate bearing (57) and the main shaft gear (22) of the external bevel gear is also attached to the rotary main shaft (20) shaft neck.
And an intermediate gear (54) that engages with them is interposed. Then, the oblique plate (40) on the circular surface (S) is attached to the housing (1).
0), the inner concave surface forming the spherical surface (G) is closed to form a half-moon-shaped working chamber (Ha) in a hemispherical space, and the half-moon-shaped working chamber (Ha) is formed on the circular surface (R) by a rotary piston (30). ) Is formed in a comb-shaped working chamber (Fu) that forms a comb-shaped space, and is further exposed to the comb-shaped working chamber (Fu).
n) and an exhaust hole (Ex) are provided, and a igniter (Ig) or a fuel injection valve is inserted and attached by checking the combustion chamber, and a spherical rotary piston engine. 5. A straight line intersecting at a spherical center (O) having a spherical surface (G) having a radius (r) with the spherical center (O) as the center of the housing (10) and having an angle (θ). The axis (X) is the axis (Y), the point where the axis (X) intersects the spherical surface (G) is the point (P), and the point where the axis (Y) intersects the spherical surface (G) is the point (Q). P) The conical locus with the diameter of the bottom surface between the points (Q) and the apex of the spherical center (O) is defined as the conical locus (U), and the distance between the points (P) and (Q) is half the diameter of the bottom surface. A conical locus having (O) as an apex is a conical locus (J), an axis line orthogonal to the axis line (X) at the spherical center (O) is an axis line (M), and a horizontal plane is formed on the axis line (X). The great circle plane in the spherical surface (G) having the axis (L) of the diameter line segment as the axis of rotation is the circular surface (R) and the axis (Y)
Is a vertical axis and a great circle plane formed through a spherical center (O) in a spherical surface (G) is a circular surface (S), and the circular surface (R) and the circular surface (S) are spherical centers (O). Intersect at and axis (M)
The axis (K) is defined as the intersecting secant forming the perpendicular line of the housing, and both ends of the intersecting secant (K) are defined as points (Ka) and points (Kb).
0), the inner wall surface of the housing (10) is formed as a rotation surface larger than a spherical surface (G) concentric with the axis (Y), and the main bearing (1) is provided on the opposite wall of the housing (10) on the axis (Y).
3) is penetrated and the housing (10) has a spherical surface (G).
Spherical Z-axis housing (7) having an inner side surface and a handle-shaped housing shaft (71) axially fixed to opposite sides on the axis (Y).
0) is rotatably fitted so that both housing shafts (71) are supported by the main bearing (13), and this Z-axis housing (70) has a portion of the inner surface along the extension plane of the circular surface (S). Orbital clearance created in the groove that orbits the car (87)
And rolling bearings (73) are provided on opposite sides on the axis (X), and the rolling bearing (73) has a straight shaft-like rolling shaft (7).
2) Axial central axis (74) which is a circular body of a pin joint joint (55) which bears both shaft necks and is positioned at the ball center (O) of the rolling shaft (72) and uses the axis (M) as a connecting shaft. ), And a spherical surface (G) on the circular surface (R) in the Z-axis housing (70).
The spherical arc surface (32) of the outer peripheral surface which is in sliding contact with the spherical arc surface (3
2) having an arcuate contour plane and having an arcuate surface (31) having a chord on the axis (K) side, and incorporating a cylindrical piston intermediate shaft (33) on the chordal side of the arcuate surface (31). A substantially plate-shaped rotary piston (30) is arranged with the rolling shaft (72) inserted therein loosely, and a piston body for receiving the circular body of the central shaft (74) in the inner center of the rotary piston (30). (35) and its piston pivot (35) is pivoted (7)
4) is pivotally mounted in a range of angle (θ) × 2 about the rolling axis (72) on the axis (X) so as to be swingable, and the points (Ka) and (Kb) at both ends of the piston intermediate shaft (33) (Kb). ) Side, a connecting element consisting of a pin or a pin receiving hole of the hinge joint (50) with the intersection secant (K) as the base axis of the joint is provided, and on the circular surface (S) in the Z-axis housing (70). Has an arcuate surface (41), an arcuate contour surface of the arcuate surface (41) and a chordal side surface (42), and an inner peripheral surface side of the arcuate contour surface is integrally connected to the Z-axis housing (70). A circular plate-shaped slanting plate (40) having an annular slanting plate ring (43) rotatably engaged with the orbital space (87) formed on the outer periphery is arranged, and the point of the slanting plate ring (43) ( When a connecting element corresponding to the connecting element of the hinge joint (50) is provided at the facing portion located at the point (Ka) (Kb) and fitted, the skew plate (40) is attached. And the rotary piston (30) are slidably connected to each other in a range of an angle (θ) × 2 with the intersecting secant (K) as an axis of the hinge, and the upper circular surface (S) is sandwiched between the opposing inner walls of the housing (10). The fixed phase gear (14) of the fixed gear is formed concentrically with the axis (Y), and the rolling gear (76) of the external gear is provided at the neck end of the rolling shaft (72) to provide the fixed phase gear (14). Then, the slanting plate (40) on the circular surface (S) closes the inner concave surface of the Z-axis housing (70) forming the spherical surface (G) to close the half-moon-shaped working chamber (Ha) in the hemispherical space. Form the half-moon shaped working chamber (H
a) is formed in a comb-shaped working chamber (Fu) in which a rotary piston (30) on the circular surface (R) forms a comb-shaped space, and is made to face the comb-shaped working chamber (Fu), and an intake hole (I) is formed.
n) and an exhaust hole (Ex) are provided, and a igniter (Ig) or a fuel injection valve is inserted and attached by checking the combustion chamber, and a spherical rotary piston engine. 6. A straight line intersecting at a spherical center (O) having a spherical surface (G) having a radius (r) with the spherical center (O) as the center of the housing (10) and having an angle (θ). The axis (X) is the axis (Y), the point where the axis (X) intersects the spherical surface (G) is the point (P), and the point where the axis (Y) intersects the spherical surface (G) is the point (Q). P) The conical locus with the diameter of the bottom surface between the points (Q) and the apex of the spherical center (O) is defined as the conical locus (U), and the distance between the points (P) and (Q) is half the diameter of the bottom surface. A conical locus having (O) as an apex is a conical locus (J), an axis line orthogonal to the axis line (X) at the spherical center (O) is an axis line (M), and a horizontal plane is formed on the axis line (X). The great circle plane in the spherical surface (G) having the axis (L) of the diameter line segment as the axis of rotation is the circular surface (R) and the axis (Y)
Is a vertical axis and a great circle plane formed through a spherical center (O) in a spherical surface (G) is a circular surface (S), and the circular surface (R) and the circular surface (S) are spherical centers (O). Intersect at and axis (M)
The axis (K) is defined as the intersecting secant forming the perpendicular line of the housing, and both ends of the intersecting secant (K) are defined as points (Ka) and points (Kb).
In (0), the inner wall surface of the housing (10) is formed into a rotation surface larger than the spherical surface (G) concentric or the axial line (Y) concentric spherical surface (G) to form a housing (10) opposing wall on the axial line (Y). The main bearing (13) is provided, and the housing (10) has an inner side surface that forms a spherical surface (G), and a partition plate-like skewed plate (61) is provided on the circular surface (S) of the inner side surface. A shaft plate chamber (64) is formed by cutting out circular recesses on opposite surfaces sandwiching a circular surface (S), and a housing bearing (63) is rotatably fitted to the center part of the side wall of the shaft plate chamber (64). A shaft that incorporates a spherical housing (60) with the axis (Y) as the axis of rotation, and the main bearing (13) and the housing bearing (63) on both sides are rotatably fitted into each of the shaft plate chambers (64). Board (2
Each of 4) is connected to the connecting rod (26) on the axis (X) to support both Z-shaped necks of the Z axis (23) and is positioned at the spherical center (O) of the Z axis (23). A pin joint joint (55) having an axis (M) as a connecting axis at the center of the connecting rod (26)
Of the circular body element is fitted onto the circular surface (R) of the housing (60), and the outer peripheral surface of the outer peripheral surface slidingly contacting the inner surface of the spherical surface (G) of the housing (60). A arcuate surface (32) and an arcuate surface (31) which forms an arcuate contour plane of the arcuate surface (32) and has a chord on the side of the axis (K), and a chord side of the arcuate surface (31). A substantially plate-shaped rotary piston (30) in which a cylindrical piston intermediate shaft (33) is integrated with is arranged by inserting the connecting rod (26) of the Z-axis (23) into the rotary piston (30). Piston pivot (35) for receiving the circular body element of the pivot connector (88) in the inner center
And its piston pivot (35) is a pivot connector (88) with the connecting rod (26) on the axis (X) as the base angle (θ) ×
2 is pivotally mounted in the range of 2 and the piston intermediate shaft (3
3) A connecting element consisting of a pin or a pin receiving hole of a hinge joint (50) having a joint base line of the intersection secant (K) is provided on both sides of the points (Ka) and (Kb) at both ends, and a housing (60). An arcuate surface (4
1) and its arcuate surface (41), the arcuate contour surface and the chordal surface (4)
2) and the housing oblique plate (61) is formed into an integral structure by fixing its arcuate contour surface to the inner surface of the housing (60), and the housing (60) has a point (Ka) point (Kb). When a connecting element corresponding to the connecting element of the hinge joint (50) is provided and fitted to the facing portion located on the) side, the skewed plate (61) of the housing in the housing (60) and the rotary piston (30) are An externally toothed bevel gear having the cross secant (K) slidably connected in an angle (θ) × 2 range with the hinge axis as a shaft, and mounted on the outer surface of the upper housing (60) around the housing bearing (63) hole as a center. Z-axis gear (27) of external bevel gear attached to the housing gear (62) and the Z-axis (23) shaft neck
And an intermediate gear (54) that engages with them is interposed, and then the skewed board (61) on the circular surface (S) is moved to the housing (6).
0), the inner concave surface forming the spherical surface (G) is closed to form a half-moon-shaped working chamber (Ha) in a hemispherical space, and the half-moon-shaped working chamber (Ha) is formed on the circular surface (R) by a rotary piston (30). ) Is formed in a comb-shaped working chamber (Fu) that forms a comb-shaped space, and is further exposed to the comb-shaped working chamber (Fu).
n) and an exhaust hole (Ex) are provided, and a igniter (Ig) or a fuel injection valve is inserted and attached by checking the combustion chamber, and a spherical rotary piston engine. 7. A straight line intersecting at a spherical center (O) having a spherical surface (G) having a radius (r) with the spherical center (O) as the center of the housing (10) and having an angle (θ). The axis (X) is the axis (Y), the point where the axis (X) intersects the spherical surface (G) is the point (P), and the point where the axis (Y) intersects the spherical surface (G) is the point (Q). P) The conical locus with the diameter of the bottom surface between the points (Q) and the apex of the spherical center (O) is defined as the conical locus (U), and the distance between the points (P) and (Q) is half the diameter of the bottom surface. A conical locus having (O) as an apex is a conical locus (J), an axis line orthogonal to the axis line (X) at the spherical center (O) is an axis line (M), and a horizontal plane is formed on the axis line (X). The great circle plane in the spherical surface (G) having the axis (L) of the diameter line segment as the axis of rotation is the circular surface (R) and the axis (Y)
Is a vertical axis and a great circle plane formed through a spherical center (O) in a spherical surface (G) is a circular surface (S), and the circular surface (R) and the circular surface (S) are spherical centers (O). Intersect at and axis (M)
The axis (K) is defined as the intersecting secant forming the perpendicular line of the housing, and both ends of the intersecting secant (K) are defined as points (Ka) and points (Kb).
In (0), the inner wall surface of the housing (10) is formed into a rotation surface larger than the spherical surface (G) concentric or the axial line (Y) concentric spherical surface (G) to form a housing (10) opposing wall on the axial line (Y). The main bearing (13) is provided, and the housing (10) has an inner side surface that forms a spherical surface (G), and a partition plate-like skewed plate (61) is provided on the circular surface (S) of the inner side surface. A spherical housing (60) having a housing bearing (63) on both opposite sides through which the axis (Y) penetrates and rotatably fitted is incorporated with the axis (Y) as a rotation axis, and main bearings on both sides ( 13) and the housing bearing (63), the shaft arms (25) each having an arbitrary shape are connected to the connecting rod (26) on the axis (X) to form a Z-shaped Z-axis (23) double-sided neck. The shaft (M) is connected to the central portion of the connecting rod (26) located at the spherical center (O) of the Z axis (23). A pivot connector (8) composed of a circular body element of a pin joint joint (55) which is an axis.
8) is externally fitted, and on the circular surface (R) in the housing (60), the spherical arc surface (32) of the outer peripheral surface and its sphere that are in sliding contact with the inner surface formed of the spherical surface (G) of the housing (60). The arcuate surface (32) has an arcuate contour plane and has an arcuate surface (31) having a chord on the axis (K) side, and a cylindrical piston intermediate shaft (33) on the chordal side of the arcuate surface (31). ) Are combined into a substantially plate-shaped rotary piston (30), which is a Z-axis (2) of the shaft arm (25) and the connecting rod (26).
3) A piston pivot (35) for inserting the circular body element of the pivot connector (88) is formed in the inner center of the rotary piston (30) by inserting the intermediate portion of the pivot pivot (35). Connect the connecting rod (2) on the axis (X) to the connector (88).
6) as a base axis so as to be swingable within an angle (θ) × 2 range, and the points (K) at both ends of the piston intermediate shaft (33).
a) On the side of the point (Kb), a pin of the hinge joint (50) having a joint secant line (K) as a joint axis or a connecting element composed of a pin receiving hole is provided, and a circular surface (S) in the housing (60). Above it is an arched surface (4
1) and its arcuate surface (41), the arcuate contour surface and the chordal surface (4)
2) and the skewed plate (61) having a box shape is integrally formed by fixing its arcuate contour surface to the inner surface of the box (60), and the point (Ka) and (Kb) of the box (60). When a connecting element corresponding to the connecting element of the hinge joint (50) is provided and fitted to the facing portion located on the side, the skewed plate (62) of the housing and the rotary piston (30) in the housing (60) are connected to each other. The crossing secant (K) is slidably connected in the range of the angle (θ) x 2 with the hinge axis as the axis of the hinge, and the external bevel gear of the upper housing (60) is attached to the outer surface of the housing bearing (63) centering the hole. External gear bevel gear Z-axis gear (27) attached to the housing gear (62) and the Z-axis (23) shaft neck
And an intermediate gear (54) having and meshing with them is interposed, and then the skewed plate (61) of the housing on the circular surface (S) is a spherical surface (G).
The inner concave surface of the housing (60) is closed to form a hemispherical working chamber (Ha) having a hemispherical space.
a) is formed in a comb-shaped working chamber (Fu) in which a rotary piston (30) on the circular surface (R) forms a comb-shaped space, and is made to face the comb-shaped working chamber (Fu), and an intake hole (I) is formed.
n) and an exhaust hole (Ex) are provided, and a igniter (Ig) or a fuel injection valve is inserted and attached by checking the combustion chamber, and a spherical rotary piston engine. 8. A straight line which has a spherical surface (G) having a radius (r) with the spherical center (O) as the center of the housing (10) and has no angle (θ) and which intersects at the spherical center (O). The axis (X) is the axis (Y), the point where the axis (X) intersects the spherical surface (G) is the point (P), and the point where the axis (Y) intersects the spherical surface (G) is the point (Q). P) The conical locus with the diameter of the bottom surface between the points (Q) and the apex of the spherical center (O) is defined as the conical locus (U), and the distance between the points (P) and (Q) is half the diameter of the bottom surface. A conical locus having (O) as an apex is a conical locus (J), an axis line orthogonal to the axis line (X) at the spherical center (O) is an axis line (M), and a horizontal plane is formed on the axis line (X). The great circle plane in the spherical surface (G) having the axis (L) of the diameter line segment as the axis of rotation is the circular surface (R) and the axis (Y)
Is a vertical axis and a great circle plane formed through a spherical center (O) in a spherical surface (G) is a circular surface (S), and the circular surface (R) and the circular surface (S) are spherical centers (O). Intersect at and axis (M)
The axis (K) is defined as the intersecting secant forming the perpendicular line of the housing, and both ends of the intersecting secant (K) are defined as points (Ka) and points (Kb).
In (0), the inner wall surface of the housing (10) is formed as a rotation surface larger than the spherical surface (G) concentric or the axial line (Y) concentric spherical surface (G) to form a housing (10) facing wall on the axial line (X). A raceway which is provided with a main bearing (13) and has an inner side surface forming a spherical surface (G) in the housing (10) and is cut into a groove that circulates an inner portion along an extension plane of a circular surface (S). A spherical phase housing (80) having a housing bearing (83) on both opposite sides through which the gap (87) and the axis (X) penetrate is rotatably fitted, and the axis (X) is incorporated as a rotation axis. Further, the main bearing (13) and the housing bearing (83) on both sides support both shaft necks of a rotary spindle (20) having a straight shaft shape, and a central portion located at the spherical center (O) of the rotary spindle (20). And a shaft center (21) consisting of a circular body of a pin joint joint (55) having an axis (M) as a connecting shaft. A circular arc surface (R) in the phase housing (80), and a spherical arc surface (32) of the outer peripheral surface which is in sliding contact with the inner surface of the spherical surface (G) of the phase housing (80) and the spherical arc surface thereof. (32) has an arcuate contour plane and has an arcuate surface (31) having a chord on the axis (K) side, and a cylindrical piston intermediate shaft (33) is provided on the chordal side of the arcuate surface (31). A combined substantially plate-shaped rotary piston (30) is arranged so as to pass through the rotary main shaft (20), and the axial center (2
1) A piston pivot (35) for receiving the circular body is formed, and the piston pivot (35) is used as an axial pivot (21) with an axis of rotation (20) on the axis (X) as a base angle (θ) × 2. Or a pin of a hinge joint (50) whose pivot axis is the intersection secant (K) on the side of the points (Ka) and (Kb) at both ends of the piston intermediate shaft (33). A connecting element composed of a pin receiving hole is provided, and an arcuate surface (41), an arcuate contour surface of the arcuate surface (41) and a chordal side surface (42) are provided on the circular surface (S) in the phase housing (80). A circular plate-shaped slanting plate (40) having an annular slanting plate ring (43) formed integrally on the outer periphery of the slanting plate ring (43) is formed by fixing the inner peripheral surface side to the arcuate contour surface. 43) is rotatably fitted in the orbital gap (87) and is located at the point (Ka) and the point (Kb) of the slanting plate ring (43). When a connecting element corresponding to the connecting element of the hinge joint (50) is provided and fitted in the opposing portion, the slanting plate (40) and the rotary piston (30) make the intersecting secant (K) the hinge axis. As the angle (θ) × 2 range is slidably connected, and the housing gear (82) of the external bevel gear and the main spindle (80) are mounted on the outer surface of the phase housing (80) centering on the housing bearing (83) hole. 20) An intermediate gear (5) having a main shaft gear (22) of an external bevel gear attached to a shaft neck and meshing with them.
4) is interposed, and then the oblique plate (40) on the circular surface (S) closes the inner concave surface of the phase housing (80) forming the spherical surface (G) to form a half-moon-shaped working chamber (Ha) in a hemispherical space. Forming a half-moon shaped working chamber (H
a) is formed in a comb-shaped working chamber (Fu) in which a rotary piston (30) on the circular surface (R) forms a comb-shaped space, and is made to face the comb-shaped working chamber (Fu), and an intake hole (I) is formed.
n) and an exhaust hole (Ex) are provided, and a igniter (Ig) or a fuel injection valve is inserted and attached by checking the combustion chamber, and a spherical rotary piston engine. 9. The rotary piston (30) has the arcuate surfaces (32), (32) on opposite sides and the arcuate surfaces (31), (31), (31), (31) on both sides. Is formed into a circular plate by interposing the piston intermediate shaft (33) on the chordal sides of two arcuate plates having a circular plate and the oblique plate (40) on the circular surface (S) is a housing (10). The half-moon-shaped working chamber (Ha) facing each other with concave surfaces forming a spherical surface (G) by dividing the inside into both sides or by dividing the inside of the casing (60) into both sides by the skewed plate (61). , (H
a) and each of the half-moon shaped working chambers (Ha), (Ha) has a comb-shaped working chamber (Fu) in which two rotary pistons (30) on the circular surface (R) form a comb shape. , (F
The spherical rotary piston engine according to any one of claims 1 to 8, which is formed into u), (Fu), or (Fu). 10. The spherical arc surface (3) in a range in which the rotary piston (30) is larger than a hemispherical surface straddling the circular surface (S).
2) has the arcuate surfaces (31), (31) on both sides of the axis (K) on the same plane of the circular surface (R) and the piston is provided between the arcuate surfaces (31), (31). The intermediate shaft (33) is joined together to form a hemispherical substantially circular plate, and the oblique plate (40) on the circular surface (S) is the housing (10).
The half-moon shaped working chamber (Ha) facing each other with concave surfaces forming a spherical surface (G) by separating the inside of the housing (60) from each other or by separating the inside of the housing (60) from both sides. ，
(Ha) and its half-moon shaped working chamber (Ha), (Ha)
9. The spherical shape according to claim 1, wherein the rotary pistons (30) on the circular surface (R) are formed in the comb-shaped working chambers (Fu), (Fu) having a comb shape. Rotary piston engine. 11. The spherical arc surface (32) on either side of the rotary piston (30) sandwiching the axis (K).
The piston intermediate shaft (33) is united with the chordal side of the arcuate plate having the arcuate surfaces (31), (31) on the front and back, and is formed into a substantially semi-circular plate, and is formed on the circular surface (S). The skew plate (40) seals the concave surface forming the spherical surface (G) in the housing (10), or the skew plate (61) seals the concave surface forming the spherical surface (G) in the housing (60). Then, the half-moon shaped working chamber (Ha) is formed, and the half-moon shaped working chamber (H) is formed.
9. A) according to claim 1, wherein the rotary piston (30) on the circular surface (R) is formed in the two comb-shaped working chambers (Fu), (Fu). Spherical rotary piston engine.