KR100609436B1 - Improvement in internal combustion engine with means of plural swinging vanes - Google Patents

Abstract

The present invention relates to an improvement of an internal combustion engine, and in particular, the structure of the engine is simplified and efficient to minimize mechanical losses and vibrations, and to provide high output while making the weight and volume of the engine as small as possible, and easy to manufacture. The present invention relates to a high efficiency, high power rotary variable wing internal combustion engine that provides such advantages.

The present invention has an enlarged radius portion 11 of the body portion (10a) having a body portion (10a) and both side plate portions (10b) having a constant radius portion on one side and an enlarged radius portion (11) on the other side; An outer diameter body 10 having an exhaust port 12 and an inlet 13 formed in place of the side plate portion 10b, and the outer diameter body 10 are eccentric to the inside of the outer diameter body 10 as a rotating material. Arranged between the circular inner diameter body 20 and the inner and outer diameter bodies 20 and 10 arranged, and each inner end thereof is restrained by a hinge portion 40 on the outer circumferential surface of the inner diameter body 20. It provides a rotary variable-wing internal combustion engine characterized in that it comprises a plurality of rotary variable blades 30 to move along the rotation of the inner diameter body (20).

Description

Rotary Variable-wing Internal Combustion Engine {IMPROVEMENT IN INTERNAL COMBUSTION ENGINE WITH MEANS OF PLURAL SWINGING VANES}

1 is a configuration diagram of an internal combustion engine according to the present invention;

2 is a cross-sectional view of main parts of an internal combustion engine according to the present invention;

3 is a perspective view of an outer diameter body of the internal combustion engine according to the present invention;

Figure 4 is a schematic diagram showing the contact position for each rotation angle of the variable blades to the outer diameter in the internal combustion engine according to the present invention,

5 is an exploded view showing the contact position relationship between the outer diameter body and the variable blade of FIG. 4;

6 is a cross-sectional view showing a preferred configuration example of a variable wing of the internal combustion engine according to the present invention;

7 (a) is a schematic configuration diagram of an internal combustion engine according to the present invention, (b) is a graph showing a change in the spatial distance between the inner and outer bodies of each stroke,

8 (a) is a schematic configuration diagram of a general piston type internal combustion engine, (b) is a graph showing a change in the space distance between the cylinder head and the piston for each stroke,

Figure 9 (a) is a schematic configuration diagram of a general vane internal combustion engine, (b) is a graph showing the change in the spatial distance between the inner and outer bodies of each stroke,

10 is a graph of changes in air pressure versus volume in general adiabatic expansion;

FIG. 11 is a graph of change in pressure versus vane area to obtain the same force due to the change in FIG. 10;

12 is a sectional view showing the main parts of the internal combustion engine according to the present invention, showing the arrangement of the nozzles;

13 is a sectional view showing the main parts of the internal combustion engine according to the present invention.

* Explanation of symbols for main parts of drawing *

1: cylinder 2: piston

3: crank 4: inner diameter

5: outer diameter 6: slit

7: vane plate 10: outer diameter

10a: main body 10b: side plate

11: enlarged radius 12: exhaust vent

13: inlet 20: inner diameter

21: inner diameter shaft 30: rotary variable wing

31: first contact surface 32: second contact surface

33: third contact surface 34: variable wing shaft

40: hinge 50: nozzle

60: globule device

The present invention relates to an improvement of an internal combustion engine, and more particularly, an inner diameter body 20 as a rotator disposed eccentrically inside an outer diameter body 10 and an inner and outer diameter body 20 ( 10 is a power generating device including a plurality of rotary variable blades 30 disposed between the movement of the inner diameter body 20, the configuration of the engine is simple and continuous combustion through the appeal device (60) ( The present invention relates to a highly efficient, high-power rotary variable-wing internal combustion engine that can use a relatively low-grade fuel and provide a high output relative to the engine weight.

The most representative of the internal combustion engine using the prior art to which the present invention belongs is a piston reciprocating internal combustion engine and a vane internal combustion engine.

8A is a schematic cross-sectional view showing a general piston type internal combustion engine composed of a cylinder 1, a piston 2, a crank 3, and the like, and (b) a crank in such a piston type internal combustion engine. (3) It is a graph showing the change of the clearance between the head of the cylinder (1) and the piston (2) according to the rotation angle of the shaft.

9A shows a slit 6 on the inner diameter body 4 between the circular inner and outer diameter bodies 4 and 5 and the inner and outer diameter bodies 4 and 5 arranged eccentrically. Is a schematic cross-sectional view showing a vane type internal combustion engine composed of a plurality of vane plates 7 arranged to linearly reciprocate, and (b) the angle of rotation of the shaft of the inner diameter body 4 in this vane type engine. It is a graph showing the change in the space distance between the outer inner body (4) and (5).

The internal combustion engines have the commonality of burning fuel to obtain thermal energy and converting it to the rotational force of the shaft by a mechanical device. Therefore, the ideal internal combustion engine is first; The most efficient power is obtained by generating continuous rotational force with an average force about the rotational axis with an explosive force each time for one cycle; Compression work, mechanical friction work, or thermal energy loss should be small; The burden of technical cost, manufacturing cost, maintenance cost and environmental cost should be small.

In this aspect, in the case of a piston type internal combustion engine, when the power generation (expansion) part of the internal combustion engine is first seen in FIG. 8 (b), the shaft corresponds to 180 ° while the axis rotates by 720 °. According to the curve, the portion in which the continuous rotational force is generated by the average force under the above conditions is only about 70 ° after the initial top dead center in FIG. This does not yield efficient rotational force, so a flywheel that maintains vibration and rotational inertia is needed, or several cylinders can compensate for this. In addition, in Fig. 8B, even in the compression stroke of the gas, since the adiabatic compression is performed at about 40 ° instead of the average compression work at a rotation angle of 180 °, the loss of the compression work is relatively large due to the sudden increase in the heat of compression. However, the piston type internal combustion engine is excellent in the sealability of the cylinder, excellent in high-pressure explosion, excellent in lubricity, cooling and durability. On the other hand, problems such as intake / exhaust system, heat loss by cooling device, elaboration of fuel mixing and explosion timing, restriction of fuel type due to sensitivity of explosion environment, necessity of advanced technology and materials, and low thermal efficiency remain problems.

In the case of the vane type internal combustion engine, the rotational force of about 90 ° is applied during one cycle of 360 °, but the curve of the expanded portion is proportional to the rotation angle. Growing. This space distance corresponds to the length of the vane plate (7). Since the pressure drops sharply with respect to a constant rotational angle after the explosion in comparison with the characteristics of the adiabatic expansion curve between the gas pressure and the volume of FIG. 10, the length of the vane plate is relatively When the pressure drops according to the curve characteristic of FIG. 11, the length of the vane plate as much as the compensation is sharply increased to generate the rotational force with the average vane plate force, thereby maximizing the mechanical rotational efficiency as described above. The efficiency is lowered, and the efficiency is also lowered by adiabatic compression at the last 40 degrees in the inverse of the expansion curve. In addition, the sliced vane plate 7 has a small amount of eccentricity and a small amount of intake air. However, by installing a plurality of vane plates 7 on one inner diameter body 4, a number of explosions are possible with respect to one rotation of the shaft, so that light weight, high output and high speed rotation can be obtained. It is required, low thermal efficiency, poor cooling, and there are problems such as wear resistance of the vane plate, side sealing of the vane plate, lubricity and the like.

The present invention, as described above, is an ideal internal combustion engine condition, converts thermal energy into efficient rotational force, effectively compresses work, minimizes energy loss, reduces mechanical friction work and heat loss, technical cost, manufacturing cost, and maintenance cost. The aim of the present invention is to provide a more improved internal combustion engine that minimizes the disadvantages of conventional internal combustion engines, with the goal of minimizing the burden of environmental costs.

First, as shown in FIG. 1, by installing a plurality of rotating variable blades 30 with respect to one rotating inner diameter body 20, the number of variable blades can be exploded at one rotation of the rotating shaft, thereby producing very high speed and high power. , The number of parts is very small.

Second, as shown in the graph of FIG. 7 (b), by manufacturing the outer diameter body 10 so that the end of the variable blade 30 moves along the inflation curve, when the explosion pressure brings about a change in the graph of FIG. The change of 30) is similar to the change in the graph of FIG. 11 to maintain the inflation curve in FIG. 7 (b) so that the pressure generates a continuous rotational force with an average force to obtain efficient mechanical energy.

Third, the exhaust port 12, the inlet port 13 and a very large exhaust port 12 and the inlet port 13 are arranged as shown in FIG. As shown in FIG. 2, the fuel is instantly exchanged with a new gas. At this time, the fuel is not mixed in the exchanged gas so that there is no leakage of fuel as in other engines.

Fourth, in Fig. 7B, the compression stroke is generally the opposite form of the ideal expansion curve, which is the curved shape of point E at point C 'on the graph of (B) and the variable rotor of the inner diameter body 20. (30) relatively increased the efficiency of the compression work because the average compression according to the rotation angle of the shaft.

Fifth, the region between the point E and the point A of FIG. 1 (top dead center) is a region of the same radius in the center of the inner diameter body 20, where the space between the rotary variable blades 30 of FIG. The outer diameter body 10 has a globule device 60 of FIG. 13, so that it is possible to use a relatively low quality fuel since the continuous combustion proceeds after ignition once at start-up.                         

Sixth, in the case of the vane type internal combustion engine, in Fig. 9 (a), the rotating internal diameter body 4 is almost impossible to cool due to the radial slit 6, but the internal diameter body of the internal combustion engine of the present invention of Fig. 1 20 is relatively easy to cool down.

Seventh, the variable blade 30 of FIG. 6 used in the present internal combustion engine of FIG. 1 has increased its eccentric force to increase its gas inflow rate, and the contact surface 31 of FIG. 6 has an inner and outer diameter body 20. According to the interval of) (10) as shown in Figure 4 is to expand this as shown in Figure 5 spread out. When the interval between the inner and outer diameter bodies 20 is narrowed, the length becomes short in the state of L ₁ , and the contact surface contacting the outer diameter body 10 becomes P ₁ , and when the width thereof becomes wide, the length becomes longer as L _6. The contact surface becomes like P _6, and the contact surface 31 of the rotary variable blade 30 reciprocates once between P ₁ and P ₆ during one rotation of the inner diameter body 20. Therefore, the wear resistance of the variable wing was made very good. And the rotary variable wing 30 of the present invention of Figure 6 is a very durable structure compared to the general vane plate (7).

Accordingly, the present invention has been studied and developed for the purpose of providing a rotary variable-wing internal combustion engine which has improved many of the above-mentioned conventional defects.

According to the present invention, the object consists of a body portion and a side plate portion having a constant radius portion on one side and an enlarged radius portion on the other side, and an ovate having an exhaust port and an intake port installed at an enlarged radius portion and a side plate portion of the body portion. A cylindrical outer diameter body (fixed body), a circular inner diameter body (rotating body) disposed eccentrically with the outer diameter body in the outer diameter body, and disposed between the inner and outer diameter bodies, respectively; It is achieved by providing a rotary variable-wing internal combustion engine, characterized in that the inner end of the configuration comprises a plurality of variable blades restrained through the hinge portion on the outer circumferential surface of the inner diameter body to move along the rotation of the inner diameter body.

Hereinafter, the internal combustion engine of the present invention will be described in more detail with reference to the embodiments illustrated in the accompanying drawings.

Figure 1 is a schematic diagram showing the basic configuration and operation principle of the internal combustion engine according to the present invention, Figure 2 is a cross-sectional view of the internal combustion engine of Figure 1 cut in different directions, Figure 3 is the internal combustion of Figures 1 and 2 It is the perspective view which showed the structural appearance of an outer diameter body in an engine.

The internal combustion engine of the present invention basically includes an outer diameter body 10 and an inner diameter body 20 and a plurality of rotary variable blades 30 arranged in a shape as illustrated in FIGS. 1 to 3. consist of.

The outer diameter body 10 is formed on the other side of the body portion (10a) and the ends of the body portion (10a) having a generally oval shape as a whole forming a radial portion (11) extended over an angle range of about 60 degrees It consists of a side plate portion 10b, the exhaust opening 12 is formed in the initial portion of the radius portion 11 enlarged in the body portion 10a of the outer diameter body 10 over an angle range of about 30 degrees. In addition, the inlet port 13 is formed in the side plate portion 10b over an angle range of about 50 ° which is slightly overlapped with the exhaust port 12 forming angle range.

At the eccentric position inside the outer diameter body 10, a circular inner diameter body 20 as a rotating body is supported and installed by the shaft 21, and between the inner diameter body 20 and the outer diameter body 10 installed as described above. A plurality of variable vanes 30 are provided at regular angle intervals.

The rotary variable blades 30 have an inner end portion of each of the rotary variable blades 30 in a state capable of rotating to one side or the other side with the hinge portion 40 as the center of rotation through the hinge portion 40. It is restrained and installed on the outer peripheral surface of 20, and the outer end part of each variable blade 30 is provided in the state which contact | connects the inner peripheral surface of the outer diameter body 10 in the state of the free end. A hinge portion 40 for restraining and coupling the inner end portion of each of the rotary variable blades 30 to the inner diameter body 20 and the configuration of the variable blades 30 installed through the hinge portion 40. , The operation is described in the Republic of Korea Patent Application No. 2003-50194 by the inventor, the configuration example of the hinge portion 40 used for the installation of the variable blade 30, the inner diameter of the variable blade 30 (20) by forming a shaft portion having a circular cross-sectional shape at the side end portion, and forming a support portion for wrapping the shaft portion of the variable blade 30 on the inner diameter body 20 such that the shaft portion of the variable blade 30 is rotatable and not freely separated. When the inner diameter body 20 rotates around the central axis by this structure, the branch body 40 rotates the variable blades 30 which are constrained by the hinge part 40 and the inner diameter body 20 which rotates. Rotating together along the outer diameter body 10 side ends of the variable blades 30 by the action of the rotating centrifugal force It is essentially the same action and is rotated in a state contacting with the inner peripheral surface of the outer body 10.

In FIG. 1, when the inner diameter body 20 rotates in a clockwise direction in the drawing and the movement of the variable blades 30 is made along the rotation of the inner diameter body 20, the outer diameter with respect to the rotation direction of the inner diameter body 20. An area of about 120 ° from the point A of the sieve 10 to the point B is an expansion zone in which the space between two adjacent rotary vanes 30 expands, and at point B The area in the range of about 60 ° to the point and point C 'is the bottom dead zone in the present internal combustion engine, and the body portion 10a of the outer diameter body 10 in the area in the range of about 30 ° to the point B to point C. In Fig. 3, as illustrated in Fig. 3, an exhaust port 12 having a substantially rectangular shape is formed, and an outer diameter body having an angle range of about 50 °, which starts slightly overlapping in an area of about 30 ° from a point C to a point C '. (10) The inlet port 13 is formed in the side plate portion 10b on both sides as shown in FIGS. There.

Then, the area in the range of about 130 ° from the point D to the point E reduces the space between two rotary variable vanes 30 adjacent to each other, such as air or a mixture of air and fuel present in the space. It forms the compression zone where the gas is compressed. The nozzles 50 are provided on both sides of the point D 'positioned at an angle of about 220 ° from the point A, with one angle difference of about half of the angle between the rotary variable blades.

This structure solves the drawbacks of fuel mixing such as the fuel mixing device using the inhalation of gas, which must be very sophisticated, the fuel used must have a certain condition, and the fuel leakage such as being sucked into the exhaust body when the exhaust and the intake stroke are performed at almost the same time. will be. Diesel engines also have very demanding conditions such as high pressure heat storage and fuel injection, injection time and injection timing. The present invention is a simple device of relatively low pressure to improve the mixing efficiency because the injection of the fuel continuously supplied through the nozzle alternately avoiding the moment when the rotary variable blade passes the nozzle.

Finally, an area of about 30 ° from point E to point A is a zone of the same radius as the top dead center in the internal combustion engine, in which the space between the variable vanes 30 is minimal. It is in a reduced state. And, between the point E and the point A, a narrow and long groove-shaped structure is formed in the center of the body portion 10a of the outer diameter body 10, and the appeal apparatus for enabling the first ignition and continuous ignition of the internal combustion engine. (燒 具 60) (60) is installed, which is a rotational variable blade 30 and the front of the rotary variable wing 30 when one rotary variable wing 30 passes through the point where the appeal device 60 is located. The hot gas already combusted in the space between the typical variable blades 30 has a double continuous combustion action that causes the gas in the space between the next rotary variable blades 30 to explode through the globule device 60. .

Figure 4 is a schematic diagram showing a state in which the rotary variable blades 30 acting upon the rotation of the inner diameter body 20 in contact with the inner peripheral surface of the outer diameter body 10 in the top dead center and the bottom dead center described above in a schematic manner. 5 is an exploded view showing the contact position relationship of the variable blades 30 with respect to the inner circumferential surface of the outer diameter body 10 in the top dead center and the bottom dead center, and FIG. 6 shows each of the rotary variable blades 30. It is sectional drawing which showed the preferable structural example of the.

As illustrated in FIG. 6, the variable blade 30 has an arc-shaped first contact surface 31 in contact with the inner circumferential surface of the outer diameter body 10 on the side facing the inner circumferential surface of the outer diameter body 10, respectively, adjacent to the rear side thereof. Such a configuration in which the second contact surface 32 of the arc contacting the first contact surface 31 of the variable blade 30 and the third contact surface 33 of the arc contacting the outer circumferential surface of the inner diameter body 10 are formed in the form shown. It is made in the form, the variable wing shaft 34 is coupled to the end portion of the inner diameter body 20 of the rotary variable wing 30 is installed in the above-described hinge portion 40 is formed.

The rotary variable wing 30 configured as described above proceeds in a state in which the first contact surface 31 is in contact with the inner circumferential surface of the outer diameter body 10 during the rotation operation along the inner diameter body 20, While reaching the point, the position where the first contact surface 31 of each of the variable blades 30 comes into contact with the inner circumferential surface of the outer diameter body 10 is P ₁ → P ₂ → P ₃ → P ₄ , as shown in FIGS. 4 and 5. → P ₅ → P ₆ is sequentially changed in the order, accordingly, the space between each of the rotary variable wing 30 also generates a corresponding continuous expansion change. The space between each of the rotary variable wing 30 is the minimum size at the top dead center and the maximum size at the bottom dead center, the rear surface of each of the variable wing 30 (inner surface facing toward the inner diameter body 20) ) Is formed in a curved shape in which the second and third contact surfaces 32 and 33 are connected to each other as in the example of FIG. 6, so that the space between the variable blades 30 is as small as possible at the top dead center. This is to be able to shrink to the size of.

Furthermore, in the present invention, each of the rotatable variable blades 30 is hinged to its rotatable variable blade shaft 34, while maintaining the complete airtightness of the high pressure gas while providing the airtightness of the hinge portion 40. Rotational movement to one side or the other side of the rotary variable wing 30 through) should be made smoothly and sufficiently strong, yet easy to manufacture, which can increase the amount of eccentricity between the inner and outer diameter bodies 20 and 10. The condition is established between the inner and outer diameter bodies 20 and 10 in the above-described aspect. In addition, the outer diameter body 10 is installed in the form of an egg shape, not a garden type, as described above.

Referring to the drawings in detail with reference to one cycle of the repeated cycle in the engine of the present invention, in Figure 1 the rotary variable wing 30 along the clockwise rotation of the inner diameter body 20 point D point E Compressed gas is mixed with the fuel between the rotary variable wing 30 while passing through, the E-point A and the point A is a top dead center zone having the same radius at the center of the inner diameter body 20, the rotary variable wing ( With the volume between 30) minimized, there is an appealing device (60) (see Fig. 13) at an appropriate location near point A of this area, which is an empty space, and the first ignition device is built and the first ignition is performed. Each time a variable rotor blade passes, it explodes in succession through this globule. The high-pressure gas generated in this way is expanded over an area of about 120 ° from the point A to the point B of FIG. 1, wherein the inner surface of the outer diameter body 10 of this region has a constant expansion degree of the rotary variable wing 30. In accordance with the rule, the inner surface of the outer diameter body 10 is formed in a form extending along the inflation curve in FIG. 7B, which generates relatively average rotational force (see FIGS. 10 and 11).

The outer diameter body 10, which has the maximum expansion at point B, has the same radius to point C '(about 60 °), and thus this zone is the bottom dead center. About 30 ° of the exhaust port 12 is located in the outer diameter body 10 from the point B to the C point of this zone as shown in Figs. 1, 2 and 3, and on both side plate portions 10b of the outer diameter body 10. The inlet 13 is arranged as shown in FIGS. 1, 2, and 3 over an angular range of about 50 °, slightly overlapping the point C and slightly exceeding the point C ', so that the rotary variable wing 30 is approximately B. There is a slight time lag between point C and point C, and exhaustion and intake are strongly performed by exhaust pressure, inertia, and centrifugal force at about the same time as in FIG. As it passes through the point C ', the rotary variable wing 30 is filled with new gas, and the angle is about 130 ° from the point D about 200 ° to the point E (about 330 ° from the point A) from the point A. In the range, the compression stroke is made. At the point D '(about 220 ° from the point A), the nozzles 50 are mounted on both side plate portions 10b at an angle of half the angle between the two rotary vanes 30. Alternately inject fuel to avoid the rotary variable wing. This simplifies the fuel supply due to the low pressure and the effect of evenly mixing the gas and the fuel by injecting the gas into a large space in order before the gas is compressed.

The outer surface of the outer diameter body 10 from the point D to the point E again has a movement curve with the free end of the rotary variable blade 30 at the center of the inner diameter body 20. Form to show a curve. Since the compression work is averaged, the energy loss is relatively small (see FIGS. 10 and 11), and at the point E, the rotary variable blade physically has a minimum radius in the axis of the inner diameter body 20. Between point E and point A, as described above, the explosion occurs again by the appeal apparatus 60 as the top dead zone. Even when a strong explosion occurs, the rotary variable wing 30 easily withstands high pressure because the third contact surface 33 of FIG. 6 is in contact with the inner diameter body 20, and this zone does not have a volume change, thus causing static expansion and an appealing device. Depending on the position of (60), the static pressure or both expansions are possible, so the thermal efficiency is high. In this way the engine continues to rotate while repeating the above process.

In general, efficient power generation conditions for internal combustion engines include: first, reducing mechanical frictional losses; second, reducing cooling energy; and third, reducing energy losses due to compression of the gas; and fourth; Effectively turning to the right.

8A is a cylinder 1 and a piston 2. FIG. A schematic cross-sectional view showing a general piston type internal combustion engine composed of a crank (3) or the like, (B) of the piston type internal combustion engine, the cylinder (1) head portion and the piston (2) according to the rotation angle of the crank (3) shaft The graph shows the change of space distance between

9A illustrates a slit on the inner diameter body 4 between the circular inner and outer diameter bodies 4 and 5 and the inner and outer diameter bodies 4 and 5 arranged eccentrically. 6 is a schematic cross-sectional view showing a general vane-type power generating engine composed of a plurality of vane plates 7 arranged to linearly reciprocate along (6). 4) It is a graph showing the change of the spatial distance between the inner and outer bodies 4 and 5 according to the rotation angle of the shaft.

The purpose of generating power through these organs is to work, and work (w) is the product of the force (f) applied to an object and the distance (s) the object has traveled by that force (w = f S). On the basis of the principle that the force f is proportional to the unit pressure and the area to which the pressure is applied, in the case of the 4-stroke piston reciprocating internal combustion engine of FIG. The angle ranges from about 70 ° to 90 ° after top dead center at the expanded portion of the graph while the axis rotates by 720 °.

In the case of the vane type engine of FIG. 9, the expansion stroke curve in the graph of (B) shows that the space distance (vane area) has to increase rapidly as the pressure rapidly decreases when the hot gas expands and the shaft rotates (FIGS. 10 and 11). Given the point, it can be seen that the characteristic of the changing curve is not correct.

On the other hand, the expansion stroke curve on the graph of Fig. 7 (b) showing the case of the internal combustion engine is similar to that of Figs. 10 and 11, so that the internal combustion engine of the present invention obtains an effective rotational force on average. have.

And, in the exhaust and intake stroke surface, in the case of the piston type internal combustion engine of Fig. 8, since the exhaust and the intake stroke are made through the 360 ° rotation of the crankshaft, there are many losses, and the existing between the cylinder (1) head and the piston (2) Because of the space part, the burned gas and the new gas are not completely exchanged. However, in the case of the present invention of FIG. 7, the intake and exhaust of the rotary variable wing 30 by the action and the exhaust pressure are similar to those of the vane type engine of FIG. 9, but the exhaust port 12 is as shown in FIGS. 2 and 3. Is large and the inlet 13 is also formed on both side plates 10b of the outer diameter body 10 at a considerable size so that the combustion gas and the new gas are almost completely exchanged at an instant, and the inner diameter of the outer diameter body 10 is also large. The amount of eccentricity of the sieve 20 can be increased, so the amount of intake and exhaust gas is much higher than that of a general vane engine.

Next, in the case of the piston-type engine of FIG. 8, the compressed stroke of the sucked gas is concentrated in the range of the last 40 degrees of the rotation angle of the crank 3 shaft 180 degrees. Falls. In the case of such a piston type engine, the number of components of the engine is very large and the weight and volume of the engine are large compared to the output.

In addition, since the compression stroke in the vane engine of FIG. 9 also works intensively in the range of about 30 °, mechanical compression work efficiency is lowered.

However, the compression stroke in the engine of the present invention shown in Fig. 7 has an average work efficiency as shown in Fig. 7B in the rotation angle range of about 120 °, so that the compression work efficiency is high.

In addition, in the engine of the present invention, at the point D '(see Fig. 1), as shown in Fig. 12, the nozzle 50 is provided with a proper angle difference between both side plate portions 10b of the outer diameter body. It is easy to use. In addition, the globule device 60 is installed at point E ~ A of Figure 1 so that the gas in the space between the rotary variable wing 30 is automatically continuously ignited while the rotary variable wing 30 is rotated, the The hot gas combusted through the groove of the globule device 60 continuously ignites and burns the gas in the left and right spaces of the rotary variable blade 30 passing through the globule device 60 over a large area of the space. By applying an average pressure to the rotary variable blades 30 (see FIG. 13), there is no torsional force in the rotary variable blades.

The internal combustion engine of the present invention as described above has the advantage that the number of components of the engine is very small, so that the mechanical loss can be minimized. In addition, the vibrations are very small, various types of fuels can be easily used, easy to manufacture, and high in mechanical efficiency. It is possible to continuously burn and explode gas, so it is possible to have high speed and high power, and that the weight and volume of the engine is small and extremely efficient compared to the power.

Claims (6)

The body part 10a and the both side plate parts 10b which formed the radial part 11 extended at one side, and correspond to the range of 120 degrees-150 degrees from the vertex position A of the said body part 10a. An exhaust port 12 is formed along the outer surface of the enlarged radius portion 11 of the body portion 10a, and an inlet port (b) is formed in the side plate portion 10b corresponding to a range of 140 ° to 190 ° from the apex position A. 13 is formed into an outer diameter body 10 of the ovate, a circular inner diameter body 20 which is eccentric with the outer diameter body 10 and disposed inside the outer diameter body 10 as a rotating material, and the inner and outer diameters Disposed between the sieves 20 and 10 and each inner end thereof is restrained and installed along the hinge portion 40 on the outer circumferential surface of the inner diameter body 20 to move along the rotation of the inner diameter body 20, The side facing the inner circumferential surface of the sieve 10 is formed in an arc shape in contact with the inner circumferential surface of the outer diameter body 10 so that the contact position with respect to the inner circumferential surface of the outer diameter body 10 depends on the distance between the inner and outer diameter bodies 10 and 20. Different Rotary variable blade internal combustion engine, characterized in that it comprises a plurality of rotary variable blades (30). According to claim 1, wherein the device for generating power to the eccentric inner body using the fluid pressure to form a top dead center zone having the shortest and the same radius from the center of the inner body on one side of the outer body 10, the other side A rotary variable-wing internal combustion engine comprising an outer diameter body that forms a bottom dead center zone having the longest and the same radius. The claim device (60) according to claim 1 or 2, wherein the appeal device (60) is provided at the apex position (A) of the top dead center (E to A section) of the outer diameter body (10). Rotating type, characterized in that the enlarged radius 11 of the outer diameter body 10 is located on the bottom dead center (B ~ C 'section) in the range of 120 ° ~ 180 ° from the installed position (A) Variable wing internal combustion engine. delete 3. The ash according to claim 1 or 2, wherein the nozzle 50 is disposed at both side plate portions 10b of the outer diameter body 10 at a position approximately 220 degrees from the apex position A. Typical variable wing internal combustion engine. 3. The circularly shaped first contact surface 31 according to claim 1, wherein each of the rotary variable blades 30 faces an inner circumferential surface of the outer diameter body 10 toward the inner circumferential surface of the outer diameter body 10. The contact position of the first contact surface 31 with respect to the inner circumferential surface of the outer diameter body 10 is changed according to the distance between the inner and outer diameter bodies 20 and 10, and the top dead center of the outer diameter body 10 ( Section E-A) to form a second arc-shaped contact surface 32 in contact with the first contact surface 31 of the adjacent variable blade 30 and a third arc-shaped contact surface 33 in contact with the outer circumferential surface of the inner diameter body 20. Rotary variable-wing internal combustion engine, characterized in that configured.

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