JPS5851135B2 - orbital rotary engine - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to an orbital rotary engine, and more particularly to an orbital rotary engine, in which a cylindrical rotating cylinder block is rotatably disposed within a cylindrical fixed casing, and a cylinder block is pierced radially around the circumference of the cylinder block. In multiple cylinders arranged radially,
A piston is provided that reciprocates by the guidance of a cam orbit provided on a cover plate attached to both sides of the casing, and as the piston reciprocates in the cylinder, the working gas is sucked,
The present invention relates to a cylinder-rotating type rotary engine in which a rotating cylinder block is configured to slide and rotate on the inner surface of a casing while performing an engine cycle of compression, explosion, expansion, and exhaust.

A wide variety of conventional rotary engines have been proposed, but
A typical example of this is Wankel's rotary piston engine, which is already in practical use.

This type of rotary engine has the advantages of fewer parts, simple structure, small volume, large output, high rotational speed, and no vibration, but the trochoidal combustion chamber shape and lubrication system are As a result, the volumetric efficiency and combustion efficiency were inferior to those of reciprocating piston engines.

In addition, in conventional engines, whether reciprocating or rotary, the stroke and motion of the piston are constant, and it is impossible to change it according to the most efficient stroke of the engine cycle. Therefore, the residual pressure of the expansion stroke cannot be fully utilized, and during the intake and exhaust strokes, the volume of the working chamber is adjusted as necessary, and the strokes are further extended to ensure sufficient suction and exhaust action. The present invention is an attempt to solve the above-mentioned drawbacks of conventional engines, particularly rotary piston engines, which have the drawback of not being able to increase efficiency. The purpose of this project is to provide a new rotary cylinder engine that overcomes the disadvantages of conventional rotary cylinders.

That is, this invention drives and rotates a plurality of pistons disposed in a cylinder block that is radially rotatable within a casing while reciprocating within the cylinder using cam orbits, as in a conventional reciprocating piston engine. The present invention also provides a cam orbit type rotary engine characterized in that the piston is configured to rotate together with the cylinder block.

Next, embodiments of the invention will be described with reference to the drawings.

As shown in FIG. 1, the orbital rotary engine of the present invention mainly includes a cylindrical fixed casing 1, a cylindrical single-turn cylinder block 2 housed in the casing 1, and a reciprocating engine within the cylinder of the cylinder block 2. A plurality of movably housed pistons 3, a pair of left and right cover plates 4 fixed to both sides of a fixed casing 10 and provided with cam grooves for reciprocating the pistons 3, and penetrating the center of the cylinder block 2. It consists of an output shaft 5.

The fixed casing 1 is a cylindrical body with support legs 11 provided on both sides of its lower part, and an intake port 12 and an exhaust port 13 are provided at appropriate locations on the circumference thereof at intervals.

On the inner peripheral surface of the casing 1, an intake groove 12a is formed from the inner end of the intake port 12 along the direction of rotation of the cylinder block 20, and an exhaust groove is formed from the inner end of the exhaust port 13 along the direction opposite to the rotation direction of the cylinder block 2. 13a (second
(see figure).

Further, a spark plug mounting hole 14 is provided at a portion of the circumferential wall forming an angle of approximately 180° with the intake port 12, and a spark plug 15 is screwed into this hole.

The fixed casing 1 is substantially an annular cylinder head, and in order to provide a good cooling effect to the fixed casing 1, a large number of cooling fins 16 are integrally connected to the casing on its outer peripheral surface.

Incidentally, on both sides of the casing 1, projections 17 for attaching the cover plate are provided at equal intervals along the circumferential direction, and a screw hole 18 is provided in the center of each projection 17. There is.

The rotating cylinder block 2 is rotatably attached to the fixed casing 1.
It is a cylindrical body housed inside, and has an annular part 21 on its outer periphery.
However, a boss portion 22 is formed in the center, and a width portion 23 is formed between the two.

A plurality of cylinders 24 are bored in the radial direction at equal intervals on the circumferential surface of the annular portion 21.
One end of 4 passes through the center of the width portion 23 and approaches the boss portion 22.

A straight guide tube 25 is provided on the width portion 23 at a position corresponding to the center line of each cylinder 24, and extends radially from the boss portion 22 toward the annular portion 21 and penetrates through the width portion 23. It is being

The length of the guide groove 25 is piston 80 stroke Marimoya S
long formed.

Further, these guide grooves 25 communicate with the lower hole of the cylinder 24, thereby forming a hollow space in the width portion 23.

The skirt portion of the piston 3 is configured to be able to move up and down in this space.

A shaft hole 26 is provided in the center of the boss portion 22, and the output shaft 5 is inserted through this hole and integrally connected to the cylinder block 2 by a spline or key means 51.

Further, a large number of cooling fins 20 are formed on both sides of the annular portion 210 and arranged radially.

Further, on the outer circumferential surface of the annular portion 21, there are two grooves surrounding the cylinder 24.
An annular groove 28a and a straight groove 28b in the axial direction are formed, and an annular gasket 29a and a straight gasket 29b are fitted into each groove 28a and 28b, respectively. Separating each cylinder 24 of the cylinder block 2,
This keeps the sliding surfaces of the cylinder block 2 and casing 1 airtight.

The piston 3 is slidably housed in the cylinder 24 of the cylinder block 2, and a piston pin 32 extends through both opposing walls of the piston 3 at the bottom of its skirt portion 31 and is rotatably supported by the walls. Both ends of the pin 320 are inserted through the straight guide grooves 25 of the width portion 23, and the ends are slidably fitted into a cam track 45 provided on the cover plate 4.

Further, several piston rings 33 are provided at the upper end of the piston 3, like a conventional reciprocating piston, to maintain airtightness between the piston 3 and the cylinder 24.

The cover plate 4 has an outer diameter approximately equal to the outer diameter of the casing 1 and is a rotary disk body, and a boss portion 42 is provided in the center thereof, and a bearing 43 is fitted into the center hole of the boss portion 42. has been done.

An annular flat portion 44 is formed around the boss portion 42, and a curved closed cam groove or cam track 45 is provided on the inner surface of the flat portion 44.

This cam track 45 is connected to the straight guide groove 25 and the cylinder 24 according to the engine cycle.
It is configured to be able to reciprocate within the cylinder block 2 and to be rotatable about the shaft 5 integrally with the cylinder block 2.

An annular protrusion 46 protruding outward is provided on the outer periphery of the flat part 44.
The other surface of this projection 46 forms an annular recess a, and the cooling fin 20 is rotatable in this recess a in accordance with the rotation of the cylinder booklet 220.

Note that a plurality of ventilation holes 47 are provided in the upper part of the protrusion 46, and cold air is forcibly guided into the recess a by these holes 47.

Further, an annular flange 48 is provided on the outermost edge of the cam raceway 45, and a screw 49 passes through the hole in the flange 48 and is screwed into the screw hole 18 provided on both sides of the casing 10, so that the left and right The cover plates 4 are attached to both sides of the casing 1.

In this way, the cover plates 4, 4 and the casing 1 constitute the engine housing, and the cylinder block 2 is rotatably housed inside the housing via the shaft 5 and the shaft 1 bearing 43.

The basic configuration of the cam track 45 is 9 as shown in FIG.
It is a closed curve formed by connecting four trochoid lines with a 0° angle as one unit, and the piston 3 can reciprocate within the cylinder 24 according to the rotation of the cylinder 220 by this trochoid orbit 450 guidance.

FIG. 5 shows a linear development diagram of the cycle according to the present invention, in which T is the locus in which the upper end of the piston advances along the track 45, and the peak of the curve is the top dead center (T, D, C). , the valley is the bottom dead center (L, D, C), S is the stroke length of the piston, A
indicates the intake start point, B indicates the end of intake, that is, the compression start point, C indicates the end of compression, that is, the ignition point and the start point of expansion, D indicates the end of expansion, that is, the exhaust start point, and E indicates the end of exhaust.

When the cylinder block 2 starts rotating from 00, as the rotation angle of the cylinder block 20 increases, the piston 3 descends from the top dead center of point A along the track 45 by being guided by the track 45o via the piston pin 32. and cylinder 2
4 is increased and the mixed gas is sucked into the cylinder 24 from the intake port 12. When the cylinder block 2 rotates 900 times and the piston 3 reaches the bottom dead center at point B, the intake stroke is completed. .

In this intake stroke, the piston 3 first leaves the intake port 12, but due to the relationship with the intake groove 12a, even if the piston 3 completely leaves the intake port 12, it continues to perform an intake action, and the piston completely moves away from the end of the intake groove 12a. Number positioning continues until you leave.

When the cylinder block 2 further rotates from point B, the piston 3 rises from point B, compressing the gas sucked into the cylinder 24, and when the cylinder block 2 rotates to 1800 degrees, the piston 3 is at the top dead center C. point and complete the compression stroke.

Next, when the compression stroke is completed, the piston 3 enters the ignition position just below the spark plug 15, and the plug 15 ignites the spark to ignite and explode the compressed mixed gas in the cylinder 24. The piston 3 is pushed down by the combustion expansion pressure of Block 2 is rotated.

When the cylinder block 2 rotates 2700 times and the piston 3 reaches from point C to point D, the expansion stroke ends.

When cylinder block 2 continues to rotate further, cylinder 2
4 enters the exhaust position below the exhaust groove 13a, the piston 3 is again guided by the track 45 and rises, and the cylinder 2
The volume inside the cylinder block 2 is gradually reduced, and the gas that has completed expansion and becomes exhaust gas is discharged to the outside of the engine from the exhaust port 13 through the exhaust groove 13a, and the cylinder block 2 rotates exactly one rotation (
360°), the piston 3 rises to the upper hole to point E and the cylinder 24 completely leaves the position of the exhaust port 13 to complete the exhaust stroke.

In this way, when the intake, compression, explosion, expansion, and exhaust strokes are successively accomplished during one rotation of the cylinder block 2, the piston 3 also returns to the intake starting point A, and the inertia of the cylinder block 2 It is guided by the two orbits 45 to perform the second cycle operation.

Due to this repeated circulation action, the piston 3 rides on the track 45 and slides back and forth within the cylinder 24, while the expansion pressure of the gas in the cylinder causes the relative induction action between the track 45 and the guide groove 25 and the momentum of the cylinder block 2. Together with this, torque in the tangential direction is generated, the cylinder block 2 is rotated, and rotational torque is output from the output shaft 5.

While the engine is operating, the heat generated inside the cylinder is radiated to the atmosphere through the cooling fins 16 and 20. However, when the cylinder block 2 rotates, the cooling fins 20 act as blower blades and cool air is radiated out. is drawn from the atmosphere into the annular space a through the ventilation hole 47, giving a forced air cooling effect to the cylinder block 2 and the cooling fin 20, and furthermore, a large number of air holes formed between the flange 48 of the cover plate 4 and the protrusion 17 of the casing are drawn into the annular space a through the ventilation hole 47. Heat is absorbed through the circumferential gap and the air is discharged as hot air. However, some of the air that has become a circular airflow in the annular space a is between the flat part 44 of the cover plate and the cylinder block. The guide groove 25 passes through the gap formed between the width portion 23 and the width portion 23.
It flows into the hollow part of the cylinder block 2 and the piston 3.
The air-cooling effect on the entire engine is significant.

Furthermore, when the piston 3 is guided by the track 45 and performs reciprocating motion, the linear guide groove 25 guides the piston so that it maintains linear motion and does not tilt.
During rotation, this guide groove 25, raceway 45 and piston pin 32
The intersecting action of the three components applies torque in the tangential direction to the cylinder block 2, causing the cylinder block 2 to rotate.

In this embodiment (Figs. 1 to 3), the cylinder block 2 is provided with four cylinders 24 and four pistons 3, so one explosion occurs every 900 revolutions of the cylinder block 2. Four explosions occur per rotation, resulting in a higher rotational speed and significantly increased power output.

In the above-mentioned embodiment, an air-cooling method is used for cooling the engine, but a water-cooling method may be used by providing a water jacket 19 inside the fixed casing 1, as shown in FIG.

In this case, the cylinder block 2 also functions as an air cooling blower, so both water cooling and air cooling work together to cool the inside and outside of the engine, resulting in an extremely good cooling effect and improving engine efficiency. can.

In addition, when a large number of cylinders are used and the volumes of the casing 1 and cylinder block 2 are not increased as much as possible, or when the casing 1 and cylinder block 2 have the smallest diameter,
When arranging a large number of pistons 3 in the same direction so that the reciprocating movement of the pistons 3 is not obstructed, the skirt portion 31 of the piston 3 is cut out at a right angle to the piston pin 32, as shown in FIG. A notch 34 is formed, and the notch 34 can prevent the skirt portions 31 from interfering with or colliding with each other while the adjacent pistons 3 are descending and reaching the bottom dead center.

In this invention, the piston 3 is always guided by the guide groove 25 and performs accurate linear movement, so unlike a conventional reciprocating piston engine, the piston relies on the skirt section, which has a device for changing the movement direction of the connecting rod and crank. Since there is no need to maintain linear motion of the piston, even if the skirt portion of the piston 3 is shortened or a notch is provided, there is no particular effect on the reciprocating motion of the piston.

In order to maintain airtightness between the cylinder block 2 and the casing 1, two annular grooves 28a are formed on the outer peripheral surface of the cylinder block 2 surrounding the cylinder 24 on each side, as shown in FIG.
, 28a, and an annular gasket (29a) in these grooves.
29a' can also be fitted.

In this case, the straight grooves and gaskets separating each cylinder may be the same as in the above embodiment.

In another embodiment of the invention, the ignition system is configured so that the mixed gas in the subsequent cylinder is ignited once when the engine is started, using part of the gas combustion flame of the preceding cylinder to burn the mixed gas. Figure 9 shows -fII of the structure.

This structure is applied when the number of cylinders 24 arranged is relatively large and two adjacent cylinders 24 are very close to each other.

In the figure, the spark plug 15 on the inner circumferential surface of the fixed casing 1 extends from the lower end of the plug hole 14 in the direction opposite to the rotational direction of the cylinder block 20, and extends from the rear end of the leading cylinder 24a to the front end of the trailing cylinder 24b. An ignition groove 10 is provided to create a flame preservation area, and this flame preservation area 10
This retains a portion of the combustion flame of the preceding cylinder 24a and ignites and burns the mixed gas in the succeeding cylinder 24b that has come within this area.

In this way, since the cylinders that have successively come to the flame holding area are ignited one after another, it is possible to continuously ignite the entire set of relays by igniting the first and second ignitions.

FIG. 10 shows another embodiment of the continuous ignition structure described above, which is a continuous ignition structure using a fuel injection method.

That is, a fuel injection nozzle 60 is provided in the flame holding area or the upper part of the rear end of the ignition groove 10, and fuel is injected into the cylinder 24, and the fuel is sucked into the cylinder 24 through the intake port 12 (see Fig. 3) and compressed air is mixed with the fuel injection nozzle 60. After mixing, it is ignited by the spark plug 15, and then the subsequent cylinder is ignited by the flame in the flame holding area 10 in the same manner as described above, so that continuous ignition can be performed like a jet engine.

In the engine with this structure, fuel is continuously supplied to the cylinder 24 via an injection nozzle 60 from an injection pump (not shown).
Injected inside.

This is explained above (not only can continuous combustion be achieved through primary ignition, but also fuels such as gasoline, diesel oil, light oil, kerosene, liquefied gas, natural gas, etc.) can be used, and the effect of octane number Since there is no detonation (damage) and there is no need to add substances such as lead that are harmful to the human body to the fuel, it can be used in a wide range of applications and has various advantages such as a long service life of the ignition device. There is.

FIG. 11 shows yet another embodiment of the present invention, in which two rotating cylinder blocks also serve as a supercharger to obtain sufficient intake action at high speed rotation.

In order to achieve this purpose, both sides of the annular portion 210 of the two cylinder blocks are formed into flat surfaces, and a large number of blades 20a and 20b are provided radially on both sides of these flat surfaces, like the blades 20 described above. The annular impeller 20A is attached with screws so as to be integrated with the two cylinder blocks, and the axial length of the casing 1A is extended so that the inner blade 20b of the impeller 2OA is included therein, with the exception that the outer blade 20
A bearing 43a is interposed between the upper inner side of the flat part 43 of the two pairs of cover plates 4 and the inner diameter of the impeller 20A, and the impeller 20A is mounted on both sides. The cylinder block 2A provided in the cylinder block 2A is configured to be rotatable on the cover plate 4 via a bearing 43a.

At the center of the output shaft 5 is a boss 22 that extends in the axial direction, passes through the shaft wall at right angles at the center of the shaft, and is connected to the two cylinder blocks.
An intake vent 52 communicating with a radial hole 22a provided in the casing is penetrated, and two annular intake grooves 12b are provided on both sides of the inner peripheral surface of the casing, facing the blade 20b. A ventilation hole 12c that communicates both the intake grooves 12a and 12b between this intake groove 12b and the intake tank 12a.
is provided.

In the engine with this structure, instead of the intake port 12, the intake hole 52 of the shaft 5 is connected to the hole 22a of the two cylinder blocks, the hollow part h, the guide groove 25, the space C between each blade 20b, and the intake groove of the casing 1A. 12b and the air intake hole 12c, the casing 1A is not provided with the above-mentioned intake port 12.

12 and 13 are partial plan views showing the main parts of the casing 1A and cylinder block 2A of the above embodiment, respectively.

When the engine with this structure is operated, air flows from the intake holes 52 and 22a through the hollow part h and the guide groove 25 to the impeller 20A due to the turbine action of the inner blade 20b of the impeller 20A, which rotates together with the two cylinder blocks. After being sucked into the inside of and increasing the pressure by the pressure increasing action of this impeller 20A,
The air enters the cylinder 24 through the annular air intake groove 12b, the air vent 12c, and the air intake groove 12a, and can fully experience the effects of a turbo supercharger.

At this time, the outer blade 20a+! Similar to the cooling fin 20 described above, it functions as a cooling blower and provides air cooling to the engine.

In this way, without changing the basic design of the two cylinder blocks, by simply installing a pair of impellers 20A on both sides, engine cooling and intake air pressure boosting can be performed at the same time, so it has practical value. is extremely high.

Figure 14 shows the implementation of this invention with heat recovery function.
Show k.

Since the engine according to the present invention always performs the intake, compression, combustion (expansion), and exhaust strokes in a fixed area, in order to fully utilize the residual heat of combustion and exhaust, and to provide a cooling effect to this high-temperature part, An intake port 12 is provided in the casing 1 in the vicinity of the spark plug 15, and a U-turn-shaped heat absorption passage 1 communicates from the intake port S to one end of the intake tank 12a on the inner peripheral surface of the casing 1 over the expansion and exhaust area of the casing 1.
2d is provided so that before the cold air enters the intake tank 12a from the intake hole 12 through the heat absorption passage 12d, a part of the waste heat radiated from the casing 1 is absorbed, thereby giving a preheating effect to the intake air.

FIGS. 15A and 15B are explanatory diagrams showing the state of movement of a piston during operation of a conventional reciprocating piston engine and an engine according to the present invention, respectively.

As can be seen from Fig. A, the piston 3A of the conventional engine performs a single chord motion due to the interlocking of the connecting rod 7 and the crank 8.

That is, when the crank 8 rotates between 00 and 9000 rotation angles, the linear velocity and displacement of the piston 3A gradually increase from zero, and reach a maximum at an angle of 90 degrees.

Thereafter, the velocity and displacement gradually decrease between 900 and 180 degrees, and become zero again at an angle of 180 degrees.

Also, between 1800 and 36000, the value goes from zero to the maximum and then goes back to zero, similar to the above 00 to 1800.

In such a single string motion, the displacement of the piston 3A becomes smaller as it approaches the top and bottom dead centers.

Therefore, at the beginning of the explosion and expansion stroke, it immediately receives a strong expansion pressure and descends rapidly, and not only is this force unable to be transmitted to the crank, but also the gradual displacement becomes resistance to the expansion gas, causing the expansion pressure to drop. This results in a loss of space.

In addition, rapid speed and displacement are required at the end of expansion and the start of the exhaust stroke, at the end of the exhaust stroke and the start of intake, and at the end of intake and compression, but the limitations of single chord motion As a result, rapid initial displacement and speed cannot be obtained at the top and bottom dead centers of the piston, so effective engine efficiency cannot be expected.

However, in this invention, as shown in FIG. 15B, the piston 3 is guided by the cam track 45 caused by the trochoidal motion and reciprocates with the same displacement even at any rotation angle of the rotating cylinder, so that the conventional single chord motion is not possible. It does not have the disadvantage that the initial displacement of the top and bottom dead center is very small, unlike the piston.

Therefore, it is possible to effectively transmit the power during combustion expansion, and there is an advantage that the resistance at the top and bottom dead centers can be reduced, and the output of the entire engine can be improved.

Although the above embodiments have described the basic embodiment in which each stroke of the piston is a constant stroke like a conventional reciprocating piston engine, in fact, the engine according to the present invention can vary the stroke of the piston by the design of the cam trajectory. So,
In order to obtain the maximum efficiency of the engine, the shape of the raceway 45 is appropriately changed, and the piston 30 stroke S is made to have long or short changes in each of the intake, compression, expansion, and exhaust strokes, or a part of them. By making the stroke longer than other strokes and by appropriately selecting the lengths of the intake groove 12a and the exhaust groove 13, the intake and exhaust times can be set to appropriate times to achieve excellent performance that best suits the desired usage conditions. You can get a new engine.

Figures 16 and 17 respectively show an example of a cam track 45 with interstage stages based on this demand and a developed diagram of an engine cycle based on this, and in this example, the track 45 is basically a trochoid. do.

However, the time occupied by the intake, compression, explosion, expansion, and exhaust strokes,
That is, the angle of rotation of the piston 3 relative to the rotation of the rotating cylinder block 2 in each stroke, and the length of the stroke of the piston 3 in each stroke are not constant, as shown in FIG. The difference is that the rotation angle is the same throughout each stroke.

In order to obtain sufficient intake air, the intake time and piston stroke are lengthened.

That is, as shown in Fig. 16.17, the intake stroke A-B
The rotation angle of the cylinder block occupied by is 90° + α,
The stroke length of the piston is Sl, and its top dead center A is slightly higher than that shown in FIG.

Also, the time of the compression stroke B-C is slightly N shorter and occupies 90°-α-β of the rotation angle of the cylinder block, the length of the piston stroke at that time is S2, and the length of the stroke S1 during intake
It's shorter than that.

When the piston reaches top dead center C and completes the compression stroke, the angle becomes 180°-β, and at this point the spark plug ignites.

This angle represented by β indicates the timing of early ignition.

At this time of ignition, the piston remains at the position aC and rotates by an angle β with the cylinder block without descending for a while.
It reaches C'.

This time gives the mixed gas in the cylinder enough time to ignite and burn, causing complete combustion and generating sufficient explosive expansion pressure. This pressure pushes the piston downward from the 01 point, and this expansion pressure This is converted into an output that rotates the output shaft 5 via the cylinder block.

In order to fully utilize this gas expansion pressure without waste, the bottom dead center at the end of the piston expansion stroke is lower than the two strokes of intake and compression, that is, piston stroke S3.
can be made longer than Sl and S2 to obtain extremely high efficiency.

Furthermore, when the expansion is completed, the piston rises from point D to point E and performs the exhaust stroke, but at this time, the exhaust gas in the cylinder must be completely exhausted (top dead center E at the end of exhaust is raised a little higher, that is, the stroke S4 of the piston is longer than each of the above-mentioned strokes S0.S2.S3, so that the piston reaches the uppermost point of the cylinder to completely eliminate the exhaust gas in the cylinder.

In other words, the portion of the piston beyond the stroke S3 is extended to perform the scavenging action.

In this way, the engine according to the present invention can arbitrarily change the operating time of each stroke and the piston stroke distance in accordance with the most effective operating conditions of the engine by deforming the orbit in the same cycle, thereby increasing the efficiency of the engine. and performance can be significantly improved and improved.

This point is completely unthinkable and impossible in conventional reciprocating histone engines and rotary piston engines.

Incidentally, the engine lubrication system of the present invention can be achieved with an extremely simple structure.

That is, the gaskets 29a, 2 of the cylinder block 2
Lubrication between 9b and the inner peripheral surface of the casing 1 can be easily achieved by providing lubricating oil holes in the casing 1 that communicate with the gasket grooves 28a and 28b, and introducing lubricating oil from outside the casing 1.

Also, for lubrication between the piston pin 32 and the groove 35, the raceway 45, and between the piston 3 and the cylinder 24, for example, lubricating oil holes are provided at the center of the shaft 5 like the air intake holes 52 and 22a shown in FIG. The lubricating oil is introduced from the shaft, and the lubricating oil is dispersed into the annular hollow part of the cylinder block 2 by the centrifugal force generated when the shaft rotates 5 times, so that the lubricating oil adheres to the raceway and the inner wall of the cylinder, thereby exerting the above-mentioned lubricating effect. can be achieved.

Further, as in conventional two-stroke engines and Wankel engines, a certain proportion of lubricating oil can be mixed into the fuel to provide lubrication.

Since these lubrication methods can be easily achieved, illustrations are omitted.

In addition, the present invention can of course be applied to fluid transport pumps, air compressors, fluid motors, etc. in addition to engines.

In this case, the cylinder block is rotated by a motor directly connected to the rotating cylinder block, fluid is sucked in from the low-pressure side suction port (intake port), and after being pressurized by the piston in the cylinder to become high-pressure fluid, the fluid is (port) to perform the action of a pump or compressor, or create high-pressure fluid with a hydraulic pump or air compressor and send it into the cylinder from the suction port to move the piston, completing work and reducing the pressure. The fluid can be circulated by discharging it from the outlet (in the case of air) or guiding it back into the pump (in the case of oil).

Since this invention has the above structure and operation, it has the following advantages and effects.

(1) It has the advantages of both conventional reciprocating piston engines and rotary piston engines, but without their disadvantages.

(2) Extremely simple structure, easy production, and low cost.

(3) High volumetric efficiency, large output torque, high rotational speed, good combustion effect, and low vibration.

(4) A large number of pistons reciprocate within each cylinder of the cylinder block and drive and rotate the rotating cylinder block by being guided by the cam track.

(5) By designing the shape of the cam orbit, the time and stroke length of the engine's intake, compression, ignition, expansion, and exhaust strokes can be changed rationally to create the most effective combination between each stroke, and the engine efficiency can be improved.

(6) The piston reciprocates within the cylinder with almost the same displacement as the cylinder block rotates, guided by the cam trajectory by the trochoid.
Efficiency is further improved because power loss is minimized in each exhaust stroke, the intake and exhaust strokes are made complete, and the power stroke can be extended.

(7) The cylinder block and output shaft are concentric and integrated, and the output is directly transmitted without relying on the crank, connecting rod, or eccentric gear transmission, so there is little loss of power and almost no vibration.

(8) Since the rotating cylinder block is equipped with both a flywheel and a cooling blower, the air cooling effect is good and there is no need to separately install a flywheel on the output shaft.

(9) In addition to having the functions of the flywheel and blower, the rotating cylinder block can also have the function of a supercharger, thereby achieving an effective intake function.

(10) The ignition system can not only ignite each cylinder individually, but also ignite the entire set of relays in sequence for subsequent cylinders that enter the ignition area with just one ignition at startup.

αυ When starting the engine, the cylinder block can be rotated directly by the starter motor or by sending compressed air into the cylinder from the intake port.

(12) When an injection nozzle is used in the ignition system, various fuels such as gasoline, diesel oil, light oil, kerosene, and liquefied gas can be used.

Each piston completes a four-stroke cycle with respect to the rotating cylinder block each revolution of the cylinder block.

[Brief explanation of the drawing]

Fig. 1 is an exploded perspective view of the rotary engine of the present invention, Fig. 2 is a partially longitudinal side view of the assembled state, Fig. 3 is a partially cutaway front view of Fig. 2, and Fig. 4 is a force 4 of the cover plate. FIG. 5 is an explanatory diagram of an embodiment showing the formation of a passage, FIG. 5 is a developed diagram for explaining the invention in detail, FIG. 6 is an explanatory diagram of the main part showing a water-cooled casing, and FIG. 8M11, FIG. 8 is an explanatory view of the main part showing a cylinder block provided with a double gasket, FIG. Fig. 9 is a longitudinal sectional front view of the main part showing another embodiment of the present invention in which a flame storage area is provided, and Fig. 11 is a partial longitudinal sectional side view of the main part of the invention in which the cylinder block functions as a supercharger. , FIG. 12 is a partially broken explanatory view of the main part of the casing shown in the embodiment shown in FIG. 11, viewed from the inner peripheral surface, and FIG.
The figures are a plan view of the main parts of the cylinder block and impeller assembly shown in the embodiment shown in Fig. 11, Fig. 14 is a cross-sectional view of the main parts of the casing with a heat recovery structure seen from the inside surface, and Fig. 15A. 15B is an explanatory diagram showing the movement of the piston and crank of the reciprocating piston engine, FIG. 15B is an explanatory diagram showing the movement of the piston according to the trajectory of the engine of the present invention, and FIG. 16 is another embodiment of the cam trajectory of the engine of the present invention. FIG. 17 is a developed view showing the relationship between the piston movement and stroke due to the cam trajectory in FIG. 16. In the figure, 1...Casing, 11-...Support leg, 12...Intake port, 12a...-Intake groove, 1310. ...Exhaust port, 13a...Exhaust groove, 15...Spark plug, 16,20.
... Cooling fin, 17 ... Protrusion, 2.2
A...”...Cylinder block, 20b...
Vane, 21... Annular part, 22... Boss part, 23... Ring part, 24... Cylinder, 25... Guide groove , 26... shaft hole, 2
9a, 29a', 29b...-Gasket,
h...Hollow surface, 3...Piston, 32
...Piston pin, 33...Piston ring, 4°°°・°゛Cover plate 42...Boss part,
43... Bearing, 44... Flat part, 45
...cam orbit, 46 ... annular protrusion,
47...Vent hole, 48...Flange part, a...Vacancy, b...Void, 5...
...-Output shaft, 51... Spline, 52.2
2a...Air passage.

Claims (1)

[Scope of Claims] 1. A cylindrical fixed casing having an intake port and an exhaust port provided at a predetermined interval on one side of a peripheral wall, and an ignition plug provided on the other side;
It is housed in the inner circumference of this fixed casing so that it can slide and rotate freely.
A rotating cylinder block of a cylindrical body having a plurality of cylinder holes extending radially through the center at predetermined intervals on a circumferential surface, and a rotating cylinder block having a cylindrical body having a plurality of cylinder holes extending radially through the center at predetermined intervals, A plurality of pistons are fitted to each other so as to be able to reciprocate and slide freely, and a piston pin is rotatably fitted to the lower end of the casing. A pair of cover plates having a cam track carved in the center thereof to guide the piston to reciprocate in the cylinder hole when the cylinder block is rotated; , in a rotary engine comprising an output shaft whose inner shaft end is rotatably supported by the bearings of the pair of cover plates, a plurality of radial cooling fins are formed on the annular outer periphery of both sides of the cylinder block, Further, radial piston guide grooves passing through both side surfaces of the block and facing each other are provided at positions corresponding to the center line of each cylinder on the annular inner peripheral edge surrounding the bearing, so that when the cylinder block is rotated, a flywheel is formed. In addition to serving as both a cooling fan and a cooling fan, a plurality of ventilation holes are provided on the annular projection surface of the casing that corresponds to the cooling fins provided on the cylinder block, and the piston pin fitted into the piston is provided with a plurality of ventilation holes. A track type rotary engine characterized in that both ends thereof pass through the piston guide groove and are slidably fitted into the cam orbits of the pair of cover plates. 2. The orbital rotary engine according to claim 1, wherein a plurality of cooling fins extending in the axial direction are further formed integrally with the casing on the outer peripheral surface of the casing. 3. The orbital rotary engine according to claim 1, further comprising a water cooling water jacket formed inside the peripheral wall of the casing. 4. On the outer circumferential surface of the cylinder block, at least two annular grooves and a plurality of axial straight grooves located between each cylinder are provided so as to surround each cylinder and separate the cylinders from each other, The orbital rotary engine according to claim 1, wherein an annular gasket and a linear gasket are respectively fitted in these grooves. 5. The orbital rotary engine according to claim 1, wherein the length of the piston guide groove is slightly longer than the stroke of the piston. 6. The orbital rotary engine according to claim 1, wherein mutually opposing notches are formed at the lower ends of both walls of the skirt portion of the piston in a direction perpendicular to the piston pin. 7 The cam track provided on the cover plate mainly guides the piston through the piston pin to make four strokes of intake, compression, expansion, and exhaust within the cylinder, that is, to make two reciprocating movements up and down each time the cylinder block rotates once. 2. The orbital rotary engine according to claim 1, wherein the orbital rotary engine is a concave groove of a sealed wet curve made of a trochoid. 8. The orbital rotary engine according to claim 7, wherein the cam trajectory is a closed curved trajectory that guides the piston so that the stroke of the piston is the same in each stroke. 9. The orbital rotary engine according to claim 7, wherein the cam orbit is a closed curved orbit that guides the piston so that the stroke in each stroke changes. 10 The cover plate is fixed by screwing the flange part into the bolt hole of the protrusion provided on the outer surface of the casing with bolts,
The orbital rotary engine according to claim 1, wherein a ventilation hole is formed between the flange portion and each projection of the casing. 11. On the inner peripheral surface of the casing, there is an ignition groove that runs from the ignition plug hole in a direction opposite to the direction of rotation of the cylinder block and is a flame holding area that communicates the rear end of the adjacent preceding cylinder with the front end of the succeeding cylinder. An orbital rotary engine according to claim 1. 12. The orbital rotary engine according to claim 11, wherein the casing is provided with a fuel injection nozzle whose tip protrudes from the rear end of the ignition groove whose tip is the flame holding area.