KR20120093174A - Opposite radial rotary-piston engine of choronski - Google Patents

Abstract

The present invention relates to an opposite radial rotary-piston engine that can be used with a generator in land vehicles, water vehicles, airplanes, etc., wherein a pair of pistons are slidably disposed inside a cylinder of a cylinder block, and these pistons move in reverse, and every piston Load depends The engine includes two rotors mounted on a guide bearing, an output shaft, and an output shaft. The inner surface of the rotor is a closed curve, and the horizontal axes of the rotor are disposed at right angles to each other. At the front of the rotor are concave surface portions made along the curve. The engine includes a T-shaped traverse, which is installed in pairs on the piston rod. Each traverse has a convex spherical protrusion, which cooperates with the recess during engine start-up. A gap is formed between the recess and the protrusion after starting the engine. The engine has support bearings, each bearing connected to each traverse. Each of the support bearings has an outer bushing rolling along the inner surface of the rotor connected to the traverse to exert a force on the rotor.

Description

Opposite Radial Rotary-Piston Engine of Choronski}

The present invention relates to an opposite radial rotary-piston engine (ORRPE) that can be used with generators in land vehicles, water vehicles, airplanes and the like.

Centrifugal pistons and rotary-piston engines (also known as ORPE) are known, which are intended to address the shortcomings of conventional piston engines. This structure has been introduced in DE3907307, US6279518, US4334506, WO005098202, RU2143572, JP7113452. For example, the last patent introduces the use of rotating the cam on an elliptical inner wall surface without the use of a crank during reciprocating motions to suppress lateral pressure on the pathtone, improve efficiency, reduce vibrations and dramatically reduce size and weight. The purpose. The remaining patents have a similar purpose.

Introduced in DE3907307 is a four-stroke engine in which the cylinder block rotates inside the rotor, the rotor is complex, has a small valve system and is not balanced with a rotating system with movable parts.

The four-stroke engine introduced in US6279518 has a valve system and a conical rotor. Figure 7 shows a conical rotor with an elliptical groove and a series of piston followers inside the groove. The device is complex, has high frictional losses, and limits the work on the part under load. Structurally, it does not eliminate the lateral force that the piston exerts on the cylinder wall.

In the four-stroke engine introduced in RU2143572, the cylinder block rotates in an elliptical trajectory and there is a rotary valve in the intake / discharge system. This structure is complex and difficult to balance. The pistons operate through rods and sliding bearings in an oval housing. High friction and heat are generated at the point of contact with the housing, shortening the life.

From the point of view of the inventors, US6161508 is an improved device of OPRE. Introduced in this patent, the disc ring is slidably installed in the valve system, one of the disc rings is fixed and the other is arranged to receive a force during the rotational movement of the rotor. The opening of the valve is determined by the manual angular position of the disc ring. According to the invention, spraying takes place through the nozzle in the fixed disk. Through-holes are formed in the valve ring, and when the fuel is ignited, the rotor reacts with the piston to form a passage between the injection nozzle and the combustion chamber.

However, this engine has some disadvantages and limitations. The engine was formed as a four-stroke engine with a cylinder block that rotated around a rotary force to power the rotor. The reaction force generated in the support bearings is very large, which may lead to shortening of lifespan. The engine uses an intake / exhaust system based on a rotary sliding valve. This requires complicated sealing means and has a very limited lifetime of up to 100 hours. Rotary cylinder blocks with linear reciprocating pistons are very difficult to balance and cause very serious vibrations. These problems can be solved by the present invention.

The reciprocating rotary engine introduced in US4334506 uses a hollow stationary block with a manifold for fuel supply and intake exhaust valves. This block supports one or more inline cylinders, with the pistons having piston rods arranged oppositely. The bearings supported on the piston rod move along the cam surface with respect to the disc, and the outer surface of the cam forms a circular cylinder. The surrounding circular cylinder provides mechanical power while rotating by the linear motion of the opposing piston. The cam surface forms a continuous trajectory that determines the movement of the piston between the top dead center and the bottom dead center. The arcuate parts at the top dead center and bottom dead center are autocycle or diesel cycles, forming a desired volume of combustion chamber or exhaust chamber during cycles according to two or four strokes. One of the disadvantages of this design is that the spark plug 48 and the fuel pipe 46 are located inside the rotor. Because of this, replacing them requires disassembling the entire engine, which makes the engine more difficult to maintain.

Another ORPE was introduced in US patent application Ser. No. 11/827595, filed on July 12, 2007 by the applicant, which converts the rotational motion of the rotor into a gradual linear stroke of the piston and vice versa. In this way, it can absorb much of the piston's lateral forces acting on the cylinder wall and show a significant improvement in weight and fuel consumption / power ratio over all currently used engines, including the Wankel rotor engine.

This patent application introduces a two-stroke counter-rotating rotary piston engine, in which the cylinder block of the engine is arranged so that two pistons move opposite to each other in one cylinder, and a common combustion chamber is formed between the heads of the pistons. A first gap is formed between the cylinder side wall and the piston, the surface of the rotor being made of a closed symmetric Cassini line (partially oval), the traverse is connected to the piston, and the roller attached to the traverse elastically presses the rotor The oil stove has an end bushing, an oil supply and discharge means, and two plungers are arranged per tube to form a second gap between the side walls of the tube, which is basically smaller than the first gap. These plungers are attached to the traverse and move oppositely, forming an external gap between the outer surface of the plunger and the bushing, an internal gap is formed between the tube side wall and the plunger inner surface, and the internal gap is connected to the oil supply means. The oil drainage means of this engine are connected to an external gap. The engine absorbs side and inertia forces, making it more efficient and clean.

However, the design of this patent application also has some disadvantages. The rotor is heavy in weight and size, and the support rolling bearings do not absorb high loads, which significantly shortens their life. Since the power is output every time the engine rotates 180 degrees, the load characteristics are uneven and the life and efficiency of the engine are reduced.

The present invention aims to provide a two-stroke opposed radial rotary-piston engine for overcoming the aforementioned disadvantages of the engine of US patent application Ser. No. 11/827595.

A pair of pistons are slidably disposed inside a cylinder of a cylinder block provided in the engine of the present invention, and these pistons move opposite to each other and have a rod for each piston. The engine includes two rotors mounted on a guide bearing, an output shaft, and an output shaft. The inner surface of the rotor is a closed curve, and the horizontal axes of the rotor are disposed at right angles to each other. At the front of the rotor are concave surface portions made along the curve. The engine includes a T-shaped traverse, which is installed in pairs on the piston rod. Each traverse has a convex spherical protrusion, which cooperates with the recess during engine start-up. A gap is formed between the recess and the protrusion after starting the engine. The engine has support bearings, each bearing connected to each traverse. Each of the support bearings has an outer bushing rolling along the inner surface of the rotor connected to the traverse to exert a force on the rotor. Other factors, such as orifices, can be added to improve engine efficiency, size and weight. The present invention can also implement a modular engine, thereby providing engines of various powers.

1A is a plan view of an assembled engine according to the present invention;
1B is a cross sectional view of the engine of FIG. 1A;
2A is a front view of the engine of the present invention;
FIG. 2B is a front sectional view of the engine of FIG. 2A; FIG.
3A is another plan view of the engine of the present invention;
3B is a cross sectional view of the engine of FIG. 3A;
4 is a perspective view of an engine according to the present invention;
4A is a perspective view of a module of another engine of the present invention;
5 is a front view and a plan view of an engine assembled with two modules according to another embodiment of the present invention;
5A is a front view and a plan view of an engine assembled with four modules according to another example of the present invention;
6 is a front view and a plan view of a power plant with two engines assembled with four modules according to another example of the invention.

1 to 4 is a preferred embodiment of the present invention, in the two-stroke internal combustion engine is characterized in that the two pistons are arranged in the opposite direction to each other, the movement of the piston is changed to the rotation of the rotor, the air injection cylinder Is characterized in that the fuel injection and liquid cooling.

This engine comprises a hollow cylinder block (1) fixed to the vehicle body, a front housing (30) and a rear housing (31) fixed to the vehicle body, a top cover (32) and a lower oil sump (33). 30 and 31 are coupled to the cylinder block 1 with bolts. The above elements are preferably made of castings. The cylinder block 1 is a power unit of the engine. The pair of four cylinders 4 are installed in the cylinder block 1 in a hot coupling manner, but in other embodiments the number of cylinders may be different.

Two pistons 6 are loosely fitted to each cylinder 4 so as to slide inside. Each piston 6 has a rod 8 and the head of the piston is located opposite the rod. As each pair of pistons 6 slides in the cylinder 4, the two rods 8 face the upper and lower openings of the sleeve 4, and each head of the two pistons 6 faces each other, The portion between both heads of the inner wall surface of the cylinder 4 constitutes a common exhaust chamber, a mixing chamber or a combustion chamber according to the operating state of the engine.

The engine's boost pump (not shown) is driven by a belt and directs air to the combustion chamber. The intake window B and the exhaust window D formed in the cylinder 4 are respectively connected to the intake channel F and the exhaust channel G formed in the cylinder block 1 (see FIG. 2B).

The orifice C of the cylinder 4 is connected to the channel F to supply air after the windows B and D are closed while the power take-off shaft, which will be described later, rotates about 6 to 7 degrees. This allows the cylinder to be filled with fresh air while rotating by the angle described above. In addition, the filling rate of the cylinder can also be basically 1.0.

In addition, the orifice C is aligned in a tangential direction to the side wall surface of the cylinder 4, which results in a line flow inside the cylinder, thereby improving the quality of fuel-air mixing. Opening and closing of the windows B and D and the orifice C is caused by the movement of the piston 6 inside the cylinder 4. The configuration, area and layout of the windows B, D and orifices C can be empirically determined for the design of the engine.

The piston 6 with the rod 8 is connected to the T-shaped traverse 7 with a screw to maintain a gap (see FIGS. 1B and 2A). Since the rod 8 is screwed into the traverse 7, the length of the rod 8 can be adjusted with the washer 12 during assembly. The washer 12 is installed on the rod 8 to adjust the compression ratio. It is used to Thus, the engine has a total of four traverses 7 (see FIG. 1B).

As shown in FIG. 4, the cylinder block 1 has a lid 25 and a plurality of through holes J. These covers 25 and the through holes J together form a cooling jacket. The cylinder block 1 has an opening E for installing the output shaft 20, which extends along the axis of symmetry of the cylinder block 1 and is perpendicular to the longitudinal axis of the cylinder 4. The cylinder block 1 of FIG. 2B includes an injector 40 to 43, a spark plug 44 to 47, a pipe for cooling liquid 55 to 58, an oil inlet pipe 39, and an air inlet pipe 36. ) And the exhaust pipe 36, both of which are installed outside the cylinder block 1 (see FIG. 4).

The output shaft 20 is rotatably installed in the cylinder block 1, and two rolling bearings 18 and 19 support the output shaft (see FIG. 3). The output shaft 20 extends through the housings 30 and 31. Sealing cuffs 15 and 24 are installed in the housings 30 and 31.

Two identical rotors 16 and 17 are fixed to the output shaft 20 by connecting materials. The transverse axes of the rotors are perpendicular to each other. Each pair of traverses 7 is connected to one rotor, which will be described later.

The inner surfaces of the rotors 16 and 17 may have a cylindrical shape with a closed curve, but may include a closed Cassini line or an ellipse having appropriate parameters. As shown in Fig. 1b, a circumferentially concave surface M is formed (by milling, etc.) on the front outer surface of each of the rotors, which surface is preferably formed in the above curve, preferably elliptical. Each of the rotors 16 and 17 is connected to two own traverses 7 (up and down), so that power is output from the output shaft every time the output shaft 20 rotates 90 degrees, thereby improving the operating efficiency of the engine and The movement is much smoother.

The pinion 21 of the auxiliary drive and the hub 22 of the flywheel 23 are fixed to the output shaft 20. Prior to installation in the engine, these elements 16-23 are assembled into a single, static and dynamic balance, avoiding or suppressing vibrations during engine operation.

As shown in Fig. 3b, each traverse 7 is provided with a projection A, with the convex spherical surface under the projection cooperating with the surface M of the rotor described above.

After starting the engine, it is preferable that the surface of the protrusion A and the surface M form a clearance of about 0.5 mm. The projection A is used for starting the engine and is not used after starting, which will be described later.

As shown in FIG. 3B, each traverse 7 is used to install a hydrolock slide 11. Hydrolock serves to reduce the inertia forces applied to the rotor at dead points, which are generated by moving traverses and pistons. This operation is described in US 11/827595.

An existing bearing 10 is installed in each traverse 7, which is preferably a slipper type and uses liquid friction. Thus, there are a total of four bearings 10 in the engine. Each bearing 10 consists of an outer cylindrical bushing, an inner cylindrical pin, and a rotational insert therebetween. The outer bushing exerts a force on the rotor while rolling on the inner surfaces of the rotors 16, 17, thereby converting the linear movement of the traverse 7 into the rotational movement of the rotor. This type of bearing increases the reliability of the diesel engine, since the bearing absorbs the high impact force of the diesel engine and maintains a rotational speed of about 40,000 to 60,000 rpm.

The construction of the traverse 7 allows the operating point between the rotor and the bearing 10 to be arranged lower than the engine of US 11 / 827,595. In addition, the load on the bearing can be reduced to reduce the size of the rotor. The rod 8 and the traverse 7 are drilled with holes of a predetermined size (see FIG. 3B), which are used for cooling and lubrication of the bearing 10.

As shown in FIG. 1B, the rod 8 is supported by guide bearings, which can support linear motion. Therefore, there are a total of eight guide bearings in the engine. Each guide bearing has a casing 26 and an axle-bushing 27, in which the bushing is pressed. The casing 26 is installed on the cover 26 with bolts (see FIG. 1A), which is basically fixed to the cylinder block 1. The guide bearing absorbs the load caused by the action of the support bearing 10 on the inner surfaces of the rotors 16 and 17 and simultaneously cools the piston 6 through the orifices drilled in the rod 8 and traverse 7. It also guides you. The fuel injection process is controlled by an existing controller (not shown).

How it works

The protrusion A of the traverse 7 plays an important role in the engine. When the engine is in the stationary position, the rotors 16 and 17 can be at any angle within 360 degrees, such that the upper piston 6 closes the inlet window B and prevents air from entering the cylinder. Thus, the rotors 16 and 17 do not act on the traverse 7 via the bearing 10, and therefore air cannot enter the cylinder. In short, the engine does not start without the projection A. In addition, while the rotors 16 and 17 are rotating, the bearing 10 may hit the rotor and damage the engine, and such breakage is prevented by the protrusion A. FIG.

After the engine stops, regardless of the position of the rotors 16 and 17, the upper traverse 7, like the piston 6 and the bearing 10, lowers due to gravity, eliminating the gap, with the protrusion A Intersects the corresponding surface M of the rotor, thereby preventing collision between them and movement of the piston 6 for opening of the inlet window B.

The engine operates as follows (see Figures 1B, 2B, 3B, 4):

When starting, the flywheel 23 transmits the rotational force to the rotors 16, 17 and the pinion 21 via the shaft 20 while rotating by an external force (e.g., electric starter, air starter, kickstarter, etc.). do. Through the belt transmission, the pinion 21 drives the supercharger to pump air into the cylinder at a pressure of about 1.4 to 1.5 kG / cm 2. This pressure range is selected for comparison with a two-stroke internal combustion engine where the crankcase has a similar pressure by the piston. The rotors 16, 17 rotate and drive the piston 6 through the projection A of the traverse 7. The movement of the piston regulates the intake of air and the exhaust of gas.

An example of the operation of the rotor 17 is shown in Fig. 1A. In this position, the piston 6 is located at the top dead center and closes the inlet window B and the outlet window D. During the rotational movement, the rotor moves the piston through the projection A to the bottom dead center position, where the inlet window B and the discharge window D open, and fresh high pressure air enters the cylinder.

The rotor then drives the bearing 10 toward top dead center, which first closes the inlet window B and then closes the discharge window B. FIG. At this time, the orifice C (shown in FIG. 2B) is opened while rotating about 6 to 7 degrees to fill the cylinder with fresh air at a filling rate of 1.0. Since this orifice is tangentially aligned with the cylinder side wall, a swirl flow of air occurs to improve the mixing of fuel and air.

As it rotates 180 degrees, the piston reaches top dead center, where air is compressed in the cylinder. Before reaching top dead center, fuel is injected into the combustion chamber of the cylinder at the command of the controller.

At this time, the fuel-air mixture is ignited and the engine starts to stroke. With this movement, the pressure of air or gas increases in the cylinder, which increases until the engine stops, and this pressure is transmitted to the outer bushing of the bearing 10 via the piston 6 and traverse 7 to the rotor ( It acts on the inner surface of 17), and the protrusion A of the traverse 7 falls off the inner surface of the rotor.

Other Embodiments

The two-stroke engine (engine) of the present invention can also be implemented in a modular manner, where several modules can be assembled into a more powerful modular engine, and several such engines can be assembled into a power plant.

Figure 4a shows a module engine (EM) of the present invention, basically half of the engine of the embodiment shown in Figures 1-4. The module engine (EM) is used to guide a cylinder block 61 with two cylinders, such as cylinder 4, and four piston rods, such as rod 8 (with casing 26 and bushing 27). Top and bottom cover 62 with four guide bearings 63 built therein, two traverses 64 (same as traverse 7) and traverse 64 assembled on two pistons (such as piston 6), respectively Two support bearings (such as bearing 10), one rotor 65 (such as rotor 16) with output shaft L (same as shaft 20), and assembled flywheel (23) Flywheel (H).

The number of said parts in the 'n'-module engine is set to n (a positive integer of 2 or more) times.

The output shaft and flywheel are manufactured separately for the module engine according to the power. For example, the two-module engine has a different shaft and flywheel than the four-module engine. The output shafts of the multi-module engines are all manufactured in one piece, or divided into several parts and then connected to each other via conventional clutches.

The axes of the rotors 65 in the case of assembling two adjacent modules form an angle to each other. In a two-module engine (same as described in the above embodiment), the angle is 90 degrees; The angle is 60 degrees in the three-module engine and the angle is 45 degrees in the four-module engine (see FIG. 5A).

In the embodiment of FIG. 5A, the angle difference is 45 degrees. For example, the angular difference between the rotors 65-11, 65-12; 65-12, 65-21; 65-21, 65-22; 65-22, 65-11 is 45 degrees. On the other hand, an angle difference of 45 degrees may be provided between the rotors 65-11, 65-21; 65-21, 65-12; 65-12, 65-22; 65-22, 65-11.

Thus, for an n-module engine, the angle difference can be 180 degrees / n, and the angle difference between the transverse axes of the rotors is arranged in a constant order between the rotors.

For example, if the engine power is from 25 hp to 250 hp, the module volume can be made into various volumes such as 50cc, 100cc, 150cc, ... 500cc. 5 shows an example of a two-module engine EM with a volume of 500 cc and a power of 250 hp, with a common axis L, flywheel H, front housing P and rear housing Z.

Generally, a power plant has k n-module engines described above, where k is a positive integer of two or more. 6 is an example of a sample power plant with two four-module engines (EM) of 500 hp each, where k is two and n is four. The two engines EM have their own output shafts L, respectively. The two output shafts are parallel to each other. Each output shaft is connected to the output gear S through an existing clutch (not shown). As shown in the bottom view of FIG. 6, an insert housing Q is provided between the two engines for receiving two or more rotors of adjacent modules of the two engines. 6 can use one or two engines depending on the power required. Depending on the installation, different types of output gears and different arrangements of output shafts are available. These facilities can be applied to trucks, buses, tanks, escalators, compact cars and airplanes with long bodies.

Claims (14)

A fixed cylinder block having a suction channel and an exhaust channel;
Four cylindrical cylinders having an inner sidewall and an inlet window and an outlet window formed on the sidewall and connected to the suction channel and the exhaust channel, respectively;
Four pairs of pistons having a rod and a head opposite the rod, the rods being arranged to slide within each of the cylinders so as to face the upper and lower openings of the cylinders, with each pair of pistons moving linearly in opposite directions with respect to each other; Four pairs of pistons forming a common combustion chamber consisting of a cylinder sidewall portion between the head and the head;
Four pairs of guide bearings installed in the cylinder block to guide linear movement of the rods;
An output shaft rotatable relative to the cylinder block;
Two identical rotors fixed to the output shaft, each having an inner surface formed in the form of a closed curve having a horizontal axis, wherein the horizontal axes of the rotor are perpendicular to each other, and a circumference formed along the curve at the front of the rotor outer surface Two rotors with shaped concave portions;
Four T-shaped traverses arranged on the rod so that the pairs are apart, the pair of traverses are connected to each rotor, each having a protrusion on the traverse, and a lower portion of the protrusion is a convex which can cooperate with the concave portion during starting of the engine. Four T-shaped traverses having a spherical surface, and a gap is formed between the concave portion and the convex spherical surface of the protrusion after engine startup; And
Four support bearings connected to each of the traverses, four support bearings having outer bushings capable of rolling movement on the inner surface of the rotor connected to the traverses coupled to the corresponding support bearings;
Two-stroke counter-radial rotary rotary piston engine, characterized in that the rolling motion of the bushing can apply a force to the rotor. 2. A two-stroke opposed radial rotary-piston engine according to claim 1, wherein an orifice is formed in the cylinder to communicate with the suction channel. 3. The two-stroke opposed radial rotary-piston engine of claim 2 wherein the orifice is aligned tangential to the sidewall of the cylinder. 2. A two-stroke opposed radial rotary-piston engine as set forth in claim 1 wherein said clearance is 0.5 mm. The two-stroke opposite radial rotary-piston engine according to claim 1, wherein the guide bearing is slipper type. The two-stroke opposite radial rotary-piston engine according to claim 1, wherein the guide bearing is slipper type. 2. The two-stroke opposite radial rotary-piston engine of claim 1 wherein the closed curve is a closed Cassini line or an ellipse. 2. The two-stroke opposite radial rotary-piston engine according to claim 1, further comprising four hydrolock slides, wherein one slide can be installed on each of the traverses. 2. The two-stroke opposed radial rotary-piston engine according to claim 1, wherein the rod and the traverse are bored with holes for lubricating and cooling the support bearings. In a two-stroke opposed radial rotary-piston engine with one module, one output shaft and two support bearings:
The module,
Fixed housing means;
A fixed cylinder block having a suction channel and an exhaust channel and assembled to the housing means;
Two cylindrical cylinders having an inner sidewall and an inlet window and an outlet window formed on the sidewall and connected to the suction channel and the exhaust channel, respectively;
Two pairs of pistons having a rod and a head located opposite the rod, the rods being arranged to slide in each of the cylinders so as to face the upper and lower openings of the cylinder, with each pair of pistons moving linearly in opposite directions relative to each other; A pair of pistons forming a common combustion chamber consisting of a cylinder side wall portion between the head and the head of the engine;
Two pairs of guide bearings installed in the cylinder block to guide linear movement of the rod;
A rotor having an inner surface formed in the form of a closed curve having a transverse axis, the front portion of the outer surface having a columnar concave portion formed along the curve; And
Two T-shaped traverses installed on the rod and connected to the rotor, each having a protrusion on the traverse, and a lower portion of the protrusion has a convex spherical surface that can cooperate with the concave portion. And two T-shaped traverses formed between the convex spheres of the protrusions.
The output shaft is rotatably supported by the housing means of the module, and the rotor is fixed to the output shaft;
The support bearings are respectively connected to the traverses, and each of the support bearings has an outer bushing capable of rolling on the inner surface of the rotor;
Two-stroke counter-radial rotary rotary piston engine, characterized in that the rolling motion of the bushing can apply a force to the rotor. In a two-stroke opposite radial rotary-piston engine with n (n is an integer greater than or equal to 2) modules, one output shaft and 2xn support bearings:
The module,
Fixed housing means;
A fixed cylinder block having a suction channel and an exhaust channel and assembled to the housing means;
Two cylindrical cylinders having an inner sidewall and an inlet window and an outlet window formed on the sidewall and connected to the suction channel and the exhaust channel, respectively;
Two pairs of pistons having a rod and a head located opposite the rod, the rods being arranged to slide in each of the cylinders so as to face the upper and lower openings of the cylinder, with each pair of pistons moving linearly in opposite directions relative to each other; A pair of pistons forming a common combustion chamber consisting of a cylinder side wall portion between the head and the head of the engine;
Two pairs of guide bearings installed in the cylinder block to guide linear movement of the rod;
A rotor having an inner surface formed in the form of a closed curve having a transverse axis, the front portion of the outer surface having a columnar concave portion formed along the curve; And
Two T-shaped traverses installed on the rod and connected to the rotor, each having a protrusion on the traverse, and a lower portion of the protrusion has a convex spherical surface that can cooperate with the concave portion. And two T-shaped traverses formed between the convex spheres of the protrusions.
The output shaft is rotatably supported by the housing means of the module, and the rotors of the module are respectively fixed to the output shaft;
The abscissas of the rotor of the module are arranged in a constant order between the rotors with an angular difference of 180 degrees / n;
The support bearings are respectively connected to the traverses, and each of the support bearings has an outer bushing capable of rolling on the inner surface of the rotor;
Two-stroke counter-radial rotary rotary piston engine, characterized in that the rolling motion of the bushing can apply a force to the rotor. 12. A two-stroke opposed radial rotary-piston engine according to claim 11, wherein said output shaft is integrally formed. 12. A two-stroke opposed radial rotary-piston engine according to claim 11, wherein said output shaft is divided into several parts, and these divided parts are connected to each other via a clutch. Output shaft gear; And
Two or more engines according to claim 11;
Each engine has its own output shaft, the output shaft being arranged in parallel with each other and connected to the output shaft gear via a clutch.

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