KR20040074573A - Rotary engine - Google Patents

Abstract

PURPOSE: A rotary engine is provided to obtain dynamic energy in an explosion and expansion process and in an exhaust process through concentric movement and to reduce the volume and the weight while obtaining high thermal efficiency and engine output. CONSTITUTION: A rotary engine comprises a housing site blocks(2,12) having more than one suction port and more than one exhaust port; more than one first shutoff valve(3) and more than one second shutoff valve(4) having a sliding surface having the same radius of curvature as a main housing(16); a shutoff valve control mechanism; a rotor(10) comprising a compression surface compressing air incoming into the inside of an engine and an expansion surface receiving expansion pressure after explosion; and a driving shaft(1) concentric with the center of a circular arc surface of the inside of the main housing. The housing site blocks constitute the engine by combining with the main housing. The shutoff valve mechanism comprises cams(9,24) controlling behavior to reduce or remove friction of the shutoff valves against the rotor; rocker arms(7,8), and shutoff valve shafts(5,6). The compression surface and the expansion surface comprise a level surface and a rotor sliding-curved surface.

Description

Rotary engine {ROTARY ENGINE}

The present invention relates to a rotary engine having a center of rotation of a drive shaft and a rotation shaft of a rotor. Most of the internal combustion engines currently used are reciprocating two-stroke or four-stroke engines, and rotary engines have eccentric drive shafts and rotating bodies.

Conventional reciprocating engines have a small internal size for the cylinder that generates mechanical energy due to the complicated mechanical configuration, and also has a limitation in the rotational speed. In addition, the mechanical loss is inevitable in the process of changing the reciprocating motion to rotational motion, there was a problem that vibration occurs. As a way of overcoming this, a rotary engine using a eccentric shaft and a housing having a trocoid curve inside has been used. Since the eccentric shaft and the rotor contact with each other do not always correspond to the direction in which the rotor is subjected to inflation pressure, the seal and the housing attached to the rotor are subjected to high pressure, and the durability is significantly lower than that of the reciprocating engine. High precision is required for the processing of the rotating body and the housing is not widely used. In addition, the capacity of the turbocharger and intercooler to compensate for the thermodynamic losses consumed in the exhaust process is limited to the extent that the exhaust process is not disturbed.

One known method for overcoming the above problem is described in US Pat. No. 6,129,067 filed by Thomas Lily. However, this type of engine has the disadvantage that the volume and size of the engine is too large compared to the exploding internal space, and can not be applied to the engine of the compression ignition method.

The present invention uses a concentric motion as a simple structure to solve the above problems, obtain mechanical energy in the explosion expansion process as well as the exhaust process, compression ignition method having a smaller volume and weight for high thermal efficiency and engine output Oriented rotary engine. Hereinafter, the configuration of a rotary engine according to an embodiment of the present invention will be described with the drawings.

1 is a simplified exploded view of a rotary engine according to the present invention.

2 is a perspective view and a cross-sectional view of the rotor in which the outer surface of the rotor protrusion is mixed with a flat surface and a free curved surface.

FIG. 3 is a single stroke of a rotary engine using the rotor of FIG. 2, in which one rotor protrusion, one first shut-off valve, and one second valve are provided in one rotor according to one embodiment of the present invention. Is an operation diagram shown in time series order,

3A is a cross-sectional view showing a rotary engine in which exhaust is in progress and immediately before compression is started;

FIG. 3B is a sectional view showing the rotary engine in a compression process in progress after the step of FIG. 3A;

FIG. 3C is a cross sectional view showing the rotary engine in a state at the end of the compression process after the step of FIG. 3B;

FIG. 3D is a cross sectional view of a rotary engine in which an explosion occurs in the explosion cavity after the step of FIG. 3C and the inflow air is at maximum compression; FIG.

FIG. 3E is a sectional view showing the rotary engine in a state where the explosion continues after the step of FIG. 3D and the expansion is started; FIG.

FIG. 3F is a sectional view showing the rotary engine in a state where expansion is in progress after the step of FIG. 3E;

Fig. 3G is a sectional view showing the rotary engine in a state just before exhaust after the step of Fig. 3F;

FIG. 3H is a sectional view showing a rotary engine in a state where exhaust is in progress after the step of FIG. 3G;

FIG. 3I is a sectional view showing the rotary engine in a state after the exhaust is in progress after the step of FIG. 3H and the first shutoff valve is in operation; FIG.

4 is a perspective view and a cross-sectional view of a rotor having an outer surface of the rotor protrusion having a circular arc surface or a free curved surface.

FIG. 5 is a rotor of one rotor projection, one first shutoff valve and one second shutoff valve in accordance with one embodiment of the present invention. FIG. An operation diagram showing the strokes in time series order,

Fig. 5A is a sectional view showing a rotary engine in which exhaust is in progress and immediately before compression is started;

FIG. 5B is a cross-sectional view showing the rotary engine in a compression process in progress after the step of FIG.

FIG. 5C is a sectional view showing the rotary engine in a state at the end of the compression process after the step of FIG. 5B; FIG.

FIG. 5D is a cross sectional view of a rotary engine in which an explosion has occurred in the explosion cavity after the step of FIG.

FIG. 5E is a sectional view showing the rotary engine in a state where the explosion continues after the step of FIG. 5D continues to expand; FIG.

FIG. 5F is a sectional view showing the rotary engine in the state of expansion heavy machinery after the step of FIG. 5E;

Fig. 5G is a sectional view showing the rotary engine in a state just before exhaust after the step of Fig. 5F;

Fig. 5H is a sectional view showing a rotary engine in a state where exhaust is in progress after the step of Fig. 5G;

Fig. 5I is a sectional view showing the rotary engine in a state after exhausting is in progress after the step of Fig. H and the first shutoff valve is in operation.

6 is a perspective view and a cross-sectional view of the rotor, wherein the outer surface of the rotor projection is a circumferential surface and the center of rotation is a circumferential center and eccentric.

FIG. 7 is a single stroke of a rotary engine using the rotor of FIG. 6, in which one rotor protrusion, one first shut-off valve, and one second valve are provided in one rotor according to one embodiment of the present invention. Is an operation diagram shown in time series order,

7A is a sectional view showing a rotary engine in which exhaust is in progress and immediately before compression is started;

FIG. 7B is a cross-sectional view showing the rotary engine in a compression process in progress after the step of FIG. 7A;

FIG. 7C is a sectional view showing the rotary engine in a state at the end of the compression process after the step of FIG. 7B;

FIG. 7D is a sectional view showing the rotary engine immediately after the explosion occurs in the explosion cavity and the inflow air is compressed to the maximum after the step of FIG. 7C;

FIG. 7E is a sectional view of a rotary engine in a state in which an explosion continues after the stage of FIG. 7D and expansion starts; FIG.

FIG. 7F is a sectional view showing the rotary engine in a state just before exhausting after the step of FIG. 7E;

FIG. 7G is a sectional view of a rotary engine in a state of exhausting after the step of FIG. 7F;

FIG. 7H is a sectional view showing the rotary engine in a state after the exhaust is in progress after the step of FIG. 7G and after the first shutoff valve is in operation; FIG.

Figure 8 is a perspective view showing only the second cam, the second shut-off valve and the second shut-off valve shaft of the rotary engine according to the present invention.

FIG. 9 is a cross-sectional view of a rotary engine provided with two rotor protrusions, two first shutoff valves, and two second shutoff valves, respectively, in one rotor according to one embodiment of the present invention.

<Description of the code | symbol about the principal part of drawing>

1. Drive shaft 2. First side housing block

3. 1st shutoff valve 4. 2nd shutoff valve

5. 1st shutoff valve shaft 6. 2nd shutoff valve shaft

7. First rocker arm 8. Second rocker arm

9. First Cam 10. Rotor

11. Rotor protrusion 12. Second side housing block

13. Intake port 14. Exhaust port

15. Cam seal housing 16. Main housing

17. Cooling water circuit 18. Explosion cavity

19. Compression chamber 20. Expansion chamber

21. Compression surface 22. Expansion surface

23. Side seal 24. Second cam

25. Spring 26. First shutoff valve peak

27. 2nd shutoff valve peak 28. 1st rotor radial point

29, 2nd rotor radius 30. Rotor central axis

31.Rotor vertex 32.Rotor sliding surface

33. Valve sliding surface 34. Smooth surface

35. Airfax seal 36. Rotor arc surface

R: Rotor Foundation Radius

1 shows an overall configuration diagram of a rotary engine according to the present invention.

The first shut-off valve 3 and the second shut-off valve 4 serve to block the compression chamber 19 which is a space in which the intake air is compressed and the expansion chamber 20 which is a space in which the air is expanded after the explosion. Do it.

Two cams 9 and 24 rotating at the same angle as the rotor intermittently move the shutoff valves 3 and 4 via the rocker arms 7 and 8 and the valve shafts 5 and 6. 8 shows a control mechanism for controlling the behavior of the second shut-off valve 4 of the entire engine. The first rocker arm 8 is equipped with a spring-not shown-so that the roller always moves in contact with the outer circumferential surface of the second cam 24. The roller of the first rocker arm 8 is always on the outer circumferential surface of the second cam. Be in touch.

The rotation of the first shut-off valve is also controlled by the rotation angle of the first cam that rotates at the same angle as the rotor in the same manner.

The injection preheating device and the nozzle, which are not shown, are provided with the injection preheating device and the nozzle, which are installed in the first housing side block 2, to increase the temperature of the fuel before the injection and to facilitate the explosion of the fuel after the injection. To be done.

The air flowing into the compression chamber 19 through the intake port 13 flows in a pre-compressed state through a supercharger using high pressure exhaust gas discharged from the exhaust port 14.

2 shows a rotor having an outer circumferential surface consisting of an arcuate surface 36, a smooth surface 34 and a valve sliding surface 33 as an embodiment of the present invention. Although the valve sliding surface 33 of the compression surface 21 and the expansion surface 22 of the rotor protrusion 11 is represented as a window arc surface in the drawing, a mechanism for controlling the behavior of a shutoff valve such as a cam according to the usage is provided. In order to receive the minimum impact force, it may be formed of an arc surface or a curved surface such as a sinusoidal curve or a higher order function of the deformed form near the arc surface. The expansion pressure of the exploded air is transmitted to the expansion surface 22 of the rotor protrusion 11, and the kinetic energy of the engine is finally transmitted to the drive shaft 1 by the rotation of the rotor 10.

The airfax seal 35 provided at the rotor vertex 31, which is the furthest point from the rotor rotation center, slides on the inner circumferential surface of the main housing 16 or on the rotor sliding surfaces 32a and 32b of the shutoff valves 3 and 4. While maintaining the airtightness of the expansion chamber 20 and the compression chamber 19, and serves to remove or minimize the friction and abrasion between the rotor projection 11 and the main housing (16). The side seal 23 maintains airtightness between the rotor 10 and the side housing blocks 2, 12 and minimizes friction and wear between the rotor 10 and the side housing blocks 2, 12. . It also prevents oil from flowing into the compression chamber 19 or the expansion chamber 20 from the drive side. This side seal 23 can be divided into a single or a plurality of parts according to production and performance requirements. In addition, the spring 25 provides an appropriate force against the seals 23 and 35 in the direction of the main housing 16 or the side housing blocks 2 and 12 so that the seals 23 and 35 are hermetically sealed. Provide adequate strength to maintain The spring of the side seal 23 is not shown.

Referring to the operation of the rotary engine configured as described above are as follows.

FIG. 3A shows a part of the compression process of the rotary engine using the rotor of FIG. 2. The air introduced into the compression chamber 19 through the step of FIG. 3I is compressed between the compression surface 21 of the rotor protrusion 11 and the second shut-off valve 4 by the rotation of the rotor 10. At this time, the second shut-off valve 4 is stopped by the action of the second cam 24 so that the air compressed in the compression chamber 19 does not flow to the expansion chamber 20. The airfax seal 35 of the rotor 10 'slides' over the inner circumferential surface of the main housing 16. In the main text, the term 'sliding' refers to a state in which a subject slides with a slight pressure on an object surface or slides while maintaining a constant gap by a given tolerance.

3b shows a state at the time when the second shut-off valve 4 starts to rotate in the same direction as the rotation direction of the rotor 10 at the end of the compression process of the rotary engine according to the present invention. The second shut-off valve 4 starts to behave by the action of the second cam 24 from the moment when the second shut-off valve peak 27 reaches the second rotor radius point 29, and the inside of the compression chamber 19 Compression continues. The rotor radius points 28 and 29 are defined as straight lines which start to change the distance between the rotor outer surface and the center of rotation of the rotor, ie the boundary between the smooth surface 34 and the rotor arc surface 36. The 1st shut-off valve 3 is stopped still.

3c shows a state in which the first shut-off valve 3 continues to be stopped and the second shut-off valve 4 rotates in the same direction as the rotor 10 as the end of the compression process of the rotary engine according to the present invention. . The radius of curvature of the rotor side of the first shut-off valve 3, that is, the rotor sliding surface 32a, is the same as the radius of curvature of the inner side of the main housing, so that the rotor vertex 31 or air during the stages of Figs. 3b to 3c. The fax seal 35 smoothly slides on the rotor sliding surface 32a of the first shut-off valve 3 while the first shut-off valve 3 is stopped.

FIG. 3D shows the compressed air compressed to the blast cavity 18 at maximum through the steps of FIG. 3C. In this case, the explosion cavity 18 may be defined as a conceptual space formed by the inner surface of the main housing 16, the outer circumferential surface of the rotor, and the outer surface of the shutoff valves 3 and 4 before and after the explosion. An injection preheater and nozzle, not shown, mounted to the housing side block 2 inject fuel into the explosion cavity 18 to combust combustion within the explosion cavity 18. Injection and combustion of the fuel is started at the point where the thermal efficiency is most increased between the states of FIGS. 3C and 3D. The first shut-off valve 3 has a first cam 9 at any point between FIGS. 3C and 3D, that is, at the moment when the first shut-off valve peak 27 reaches the rotor vertex 31 or the airfax seal 35. It begins to behave by the action of). Since the rotor slide curved surface 33 of the rotor protrusion 11 is a curved surface close to an arc such as an arc and a deformed sine curve. The impact force applied to the rocker arms 7 and 8 and the cams 9 and 24 is minimized while the vertices 26 and 27 of the shutoff valve slide on the rotor slide surface 33.

The compression ratio and combustion characteristics of the rotary engine according to the present invention can be adjusted by changing the shape of the curved surface of the explosion cavity 18.

Fig. 3E shows the state after the step of Fig. 3D, the combustion continues, and the expansion of the combusted air is started. 3d to 3e, the first shut-off valve 3 and the second shut-off valve 4 rotate to contact the outer surface of the rotor 10 by the action of the cam, or rotate while maintaining an extremely small gap. do. The apex 31 or the airfax seal 35 of the rotor protrusion 11 slides on the rotor radial arc surface of the second shut-off valve 4, that is, on the rotor sliding surface 32b. The first shut-off valve 3 is stopped from the moment when the vertex 26 of the first shut-off valve reaches the first rotor radius point 28.

3F shows the engine in the middle of the expansion process. The stop state of the 1st shut-off valve 3 and the 2nd shut-off valve 4 is continued.

Fig. 3G shows the engine in a state just before the exhaust is started. The stop state of the 1st shut-off valve 3 and the 2nd shut-off valve 4 is continued.

In Fig. 3H, the exhaust is continued, and the engine with the second shut-off valve 4 rotating in the rotor direction from the state of Fig. 3G is shown.

In Fig. 3i, the exhaust is continued, and the first shut-off valve 3 is rotated from the state of Fig. 3h to show the engine in contact with or near the rotor. Rotation of the first shut-off valve 3 is started after the rotation of the second shut-off valve 4 is finished so that there is no phenomenon in which the new chamber of the compression chamber 19 and the exhaust gas of the expansion chamber 20 are mixed. The rotary engine according to the present invention generates an effective torque even in the exhaust process after the step of Fig. 3g, and because the rotation of the rotor is not hindered regardless of the capacity of the supercharger connected to the exhaust port 14, it is higher than the conventional engine. It is possible to introduce pressure air into the compression chamber 19. After the step of Fig. 3i, the engine proceeds to the state of Fig. 3a and the compression is continued. The process as described above is repeated continuously.

In the above, the outer surface of the rotor protrusion 11 exemplifies a circular rotary engine using the rotor 10 in which the smooth surface 34 and the arc surface 33 or the smooth surface 34 and the free curved surface 33 are mixed. The form of can be changed according to usage and functional requirements. The following illustrates an embodiment in which the outer peripheral surface of the rotor is composed of an arc surface and a free surface.

4 shows a rotor whose outer surface of the rotor protrusion 11 is formed of an arc surface or a free curved surface without a smooth surface. The configuration and action of the rotor protrusion 11, the seals 23 and 35 and the spring 25 are as described with reference to FIG.

FIG. 5 is an operation diagram of the rotary engine using the rotor of FIG. 4, and other configurations except for the rotor are the same as FIG. 3.

Figure 5a shows part of the compression process. The air introduced into the compression chamber 19 through the step of FIG. 5I is compressed between the compression surface 21 of the rotor protrusion 11 and the second shut-off valve 4 by the rotation of the rotor 10. At this time, the second shut-off valve 4 is stopped by the action of the second cam 24 so that the air compressed in the compression chamber 19 does not flow to the expansion chamber 20. The first shut-off valve 3, which behaves depending on the rotational angle of the first cam 9, is also stopped.

5b shows a state at the time when the second shut-off valve 4 starts to rotate at the end of the compression process of the rotary engine according to the present invention. At this time, the 1st shut-off valve 3 is stopped and the compression in the compression chamber 19 is continued. The second shut-off valve 4 starts to rotate from the moment when the vertex 27 passes the second rotor radius point. The rotor radius points 28 and 29 are defined as straight lines on the rotor outer surface which vary the distance between the rotor outer surface and the rotor rotation center, that is, the boundary between the rotor arc surface 36 and the compression surface 21. The 1st shut-off valve 3 is stopped still.

Figure 5c shows the state of the end of the compression process of the rotary engine according to the present invention. The first shut-off valve 3 is still stopped, and the second shut-off valve 4 rotates at a slight rotational angular speed.

In FIG. 5D, the compressed air is maximally compressed into the explosion cavity 18. The first shut-off valve 3 behaves by the action of the first cam 9 at any point between FIGS. 5C and 5D, i.e., at the moment when the first shut-off valve peak 27 reaches the rotor peak 31. Beginning, the injection preheater and nozzle mounted to the housing side block 2 inject fuel into the explosion cavity 18 to combust combustion in the explosion cavity 18. Injection and combustion of fuel is initiated at the point where thermal efficiency is most increased between FIGS. 5C and 5D.

Fig. 5E shows a state in which combustion of compressed air and expansion of combusted air are started. While the state of FIG. 5D to FIG. 5E is reached, the first shutoff valve 3 and the second shutoff valve 4 rotate to contact the outer surface of the rotor 10 or rotate while maintaining an extremely small gap. The second shut-off valve 4 is stopped when the rotor peak 31 or the airfax seal 35 reaches the second shut-off valve peak 27. The apex 31 or the airfax seal 35 of the rotor then slides on the arc radius side of the rotor of the second shut-off valve 4, ie on the sliding surface 32b.

Figure 5f shows the engine in the middle of the expansion process. The stopped state of the second shut-off valve 4 continues. The first shut-off valve 3 is stopped from the moment when the vertex 26 of the first shut-off valve reaches the first rotor radius point 28.

Fig. 5G shows the engine in the state just before the exhaust is started. The stop state of the 1st shut-off valve 3 and the 2nd shut-off valve 4 is continued.

In Fig. 5H, the exhaust is continued, and the engine in the state in which the second shut-off valve 4 rotates in the same direction as the rotation direction of the rotor from the state in Fig. 5G is shown.

Exhaust continues in FIG. 5I, and the state after the first shut-off valve 3 is rotated from the state in FIG. 5H is shown. The rotation of the first shut-off valve 3 is started after the rotation of the second shut-off valve 4 is finished.

Even in this embodiment, an effective torque is also generated in the exhaust process after Fig. 5G, and the rotation of the rotor is not disturbed regardless of the capacity of the supercharger connected to the exhaust port 14, so that air of a higher pressure than in a conventional engine is generated. It is possible to flow into the compression chamber 19.

After the step of Fig. 5i, the engine proceeds to the state of Fig. 5a and the compression is continued. The process as described above is repeated continuously.

FIG. 6 shows a rotor in which the outer surface of the rotor protrusion 11 has a circumferential surface only. The axis of rotation of the rotor and the center of the rotor circumference are eccentric, and the amount of eccentricity is equal to the difference between the inner radius of the main housing and the radius of the rotor circumference. The configuration and action of the rotor protrusion 11, the seals 23 and 35, and the spring 25 are as described with reference to FIGS. 2 or 4.

7 is an operation diagram of the rotary engine using the rotor of FIG. 6, and other configurations except for the rotor are the same as those of FIG.

7A and 7B show part of the compression process. The air introduced into the compression chamber 19 through the step of FIG. 7H is compressed between the compression surface 21 of the rotor protrusion 11 and the first shut-off valve 3 by the rotation of the rotor 10. At this time, the second shut-off valve 4 rotates in the same direction as the rotor so as to contact the rotor compression surface 21 by the action of the second cam 24. The 1st shut-off valve 3 which acts according to the rotation angle of the 1st cam 9 is stopped.

Figure 7c shows the state at the end of the compression process of the rotary engine according to the invention. The first shut-off valve 3 continues to stop for the period from FIG. 7B to FIG. 7C, and starts to rotate after the rotor vertex 31 passes the first shut-off valve peak 26. The second shut-off valve 4 rotates at a very slight rotational angular speed.

FIG. 7D shows the state after the injection preheating device and the nozzle mounted on the housing side block 2 inject fuel into the explosion cavity 18 to start combustion. Injection and combustion of the fuel is started at the point where the thermal efficiency is most increased between FIGS. 7C and 7D. After the rotor peak 31 or the airfax seal 35 reaches the second shutoff valve peak 27, the second shutoff valve 4 stops. The apex 31 or the airfax seal 35 of the rotor then slides on the circular arc surface of the rotor of the second shut-off valve 4, that is, on the sliding surface 32b. The first shut-off valve 3 rotates in the same direction as the rotor 10 so as to contact the rotor by the action of the first cam 9.

Fig. 7E shows a state in which combustion of compressed air and expansion of combusted air are started.

Fig. 7F shows the engine in a state just before the exhaust is started. The stop state of the second shut-off valve 4 continues, and the first shut-off valve peak 26 rotates in the same direction as the rotor so as to keep in contact with the outer surface of the rotor.

In Fig. 7G, the exhaust is continued, and the engine in the state in which the second shut-off valve 4 rotates in the same direction as the rotor from the state in Fig. 7F is shown.

In FIG. 7H, the exhaust continues, and the state after the first shut-off valve 3 rotates in the opposite direction to the rotor is shown. The rotation of the first shut-off valve 3 is started after the rotation of the second shut-off valve 4 is finished. After the step of FIG. 7H, the engine proceeds to the state of FIG. 7A and compression is continued. The above process is repeated repeatedly.

In the above, an example in which one rotor protrusion 11, one first shut-off valve 3, and a second shut-off valve 4 is provided in one rotor 10 has been described. The number 11 and the shutoff valves 3 and 4 may be one or more than two, an example of which is illustrated in FIG.

The above embodiment is for illustrating the present invention, and the present invention is not limited to this embodiment. Various modifications and variations of the present invention will be apparent to those skilled in the art without departing from the scope and spirit of the invention, which modifications and variations fall within the spirit and scope of the invention as defined by the appended claims.

In the rotary engine according to the present invention, since the rotor vertex 31 or the airfax seal 35 rotates while maintaining a uniform gap on the rotor sliding surface 32 or the inner surface of the housing, or rotates with a constant pressure, the conventional rotary engine In contrast, a significantly higher durability is expected. In addition, the supercharger (not shown) attached to the exhaust port 14 does not interfere with the rotation of the rotor even when using a large capacity unlike the conventional engine, so that the thermodynamic energy of the exhaust gas is higher than that of the conventional engine. It is possible to convert and use mechanical energy with efficiency, and it is possible to introduce intake air at a higher pressure than a conventional engine. In addition, unlike the reciprocating engine, since the intake and exhaust mechanism is naturally adjusted by the rotation angle of the rotor itself without a separate mechanism, the weight and size of the engine can be expected to be smaller and smaller.

Claims (5)

A circular rotary engine that is compressed and ignited, One or more intake ports 13 and one or more exhaust ports 14, the main housing 16 of which a majority of the inner surface has a circular shape, and the housing site blocks 2, 12 coupled with the housings to constitute the engine. )and, One or more first shut-off valves 3 and one or more second shut-off valves 4 provided with a sliding surface 32 having the same radius of curvature as the main housing, Shut-off valve control mechanism composed of cams (9,24), rocker arms (7,8), and shut-off valve shafts (5,6) for controlling the behavior of the shut-off valves (3,4) so that friction is minimal or not against the rotor Wow, Compression surface 21 for compressing the air introduced into the engine and the expansion surface 22 receives the expansion pressure after the explosion, The compression surface 21 and the expansion surface 22 is a rotor 10 composed of a smooth surface 34 and a rotor slide surface 33 which is a free curved surface, A rotary engine composed of a drive shaft (1) concentric with the center of an arc surface of a housing inner surface. The rotary engine (10) of claim 1, wherein the rotor (10) is provided with an airfax seal (35) and a side seal (23). 3. The rotary engine according to claim 1 or 2, wherein the compression surface (21) and the expansion surface (22) of the rotor (10) are composed of an arc surface and a free curved surface. 3. The rotary engine according to claim 1 or 2, wherein the outer circumferential surface of the rotor (10) is composed of a circumferential surface and the rotating shaft (1) of the rotor and the rotor circumferential center are eccentric. Rotary engine according to claim 1 or 2, characterized in that it comprises a plurality of rotors (10) and a plurality of housings (16).