WO2005038212A1

WO2005038212A1 - Rotary engine

Info

Publication number: WO2005038212A1
Application number: PCT/KR2004/002620
Authority: WO
Inventors: Han Young Park
Original assignee: Han Young Park
Priority date: 2003-10-15
Filing date: 2004-10-14
Publication date: 2005-04-28

Abstract

The present invention discloses a rotary engine, and more particularly, a rotary engine with a crank linked to a main shaft operating a vane homogeneously to maintain a gap between the rotor and the vane closely and constantly not only to maximize compression efficiency but also to provide constant homogeneous compression force, distributing compression force transferred to the vane homogeneously to make the vane slide smoothly with the rotor, installing a sealing means to the vane elastically to keep sealing states between the vane and the rotor not only to prolong a lifespan of the rotary engine but also to lower pulsation generated by pressure difference between a suction chamber and a compression chamber, and improving the shape of the rotor not only to inhale enough amount of air but also to exert high compression force to embody high output power and high speed rotation.

Description

Title

ROTARY ENGINE Field of the Invention

The present invention relates to a rotary engine, and more particularly, a rotary engine with a crank linked to a main shaft operating a vane homogeneously to maintain a gap between the rotor and the vane closely and constantly not only to maximize compression efficiency but also to provide const-ant homogeneous compression force, distributing compression force transferred to the vane homogeneously to make the vane slide smoothly with the rotor, installing a sealing means to the vane elastically to keep sealing states between the vane and the rotor not only to prolong a lifespan of the rotary engine but also to lower pulsation generated by pressure difference between a suction chamber and a compression chamber, and improving a shape of the rotor not only to inhale enough amount of air but also to exert high compression force to embody high output power and high speed rotation. Description of the Related Art

Generally, one of the methods improving entire efficiency of a normal internal combustion engine of volume conversion type is to replace a reciprocation motion of a piston of the internal combustion engine with a rotational motion, so that energy by high pressure of an expanded combustion gas drives a driving shaft directly. By referring to Fig. 1, an example of a configuration of a conventional rotary engine rotating the driving shaft will be described briefly in the following statements. The conventional rotary engine comprises a cylinder 10 including an inlet port in one side and an outlet port in the other side, a rotor 20 installed in a main shaft within the cylinder 10 to rotate eccentrically following to the inner circumference of the cylinder 10, and a vane 30 operating with the rotation of the rotor 20 within the cylinder 10 to organize a compression chamber and a suction chamber. According to the usage of the conventional rotary engine, a check valve supplying a compressed fluid to the outside selectively, or an ignition means exploding a mixed fluid compressed within the compression chamber is installed in a predetermined position of the compression chamber of the cylinder 10 While the rotor 20 of the conventional rotary engine rotates, the outer circumference of the rotor 20 is closely contacted with the proximity of the vane 30 to maintain sealing states of the compression chamber. At this case, to maintain the sealing states between the rotor 20 and the vane 30 effectively, a spring (not shown) is applied between the cylinder 10 and the vane 30. However, when the spring is applied to make the rotor 20 contact closely with the vane 30, not only the proximity of the vane 30 is rapidly worn to hardly maintain sealing states within the compression chamber, but also the strong contact force between the rotor 20 and the vane 30 gives a heavy load to the rotation of the rotor 20. As a result, there is a problem that the lifespan of the conventional rotary engine is shortened. In more, when the sealing states between the rotor 20 and the vane 30 is hardly maintained by abrasion of the proximity of the vane 30, combustion states is very poor, and explosive force within the compression chamber is heavily lowered. As a result, the conventional rotary engine becomes to have lowered efficiency and increased energy consumption to make widely spread usage of the conventional rotary engine hard and difficult. Additionally, another conventional rotary engine shown in Fig. 2 is disclosed at Japanese Patent Application No. Pyung 10-311224. The rotor 20 of this disclosed rotary engine is protruded to the one direction only from a circle shape to form a hydraulic pressure header 26. However, because the contact time between the hydraulic pressure header 26 and the suction rotator 23 is remarkably short, compression force is low and a little amount of a fluid is compressed. Therefore, this disclosed rotary engine can not be used to exert high output .

Detailed Description of the Invention

To overcome the above described problems, preferred embodiments of the present invention provide a rotary engine with a crank linked with a main shaft operating a vane homogeneously to keep a gap between the rotor and the vane closely and constantly not only to maximize compression efficiency but also to provide constant homogeneous compression force. Other purpose of the present invention is to provide a rotary engine installing a turbine wheel at the main shaft rotated by high pressure of an outlet gas to enhance rotatory power of the main shaft, and a compressor wheel at the main shaft to supply forcedly fuels with the inhaled compressed air to an inlet port of a cylinder not only to simplify the conventional mechanical complexity of using extra driving means to rotate the compressor wheel, but also to reduce the entire volume of the conventional rotary engine . Another purpose of the present invention is to provide a rotary engine distributing a compression force transferred to the vane homogeneously to make the vane slide smoothly with a rotor, installing a seal means to the vane elastically to keep sealing states between the vane and the rotor not only to prolong a lifespan of the rotary engine but also to lower pulsation generated by pressure difference between a suction chamber and a compression chamber, and improving a shape of the rotor not only to inhale enough amount of air but also to exert high compression force to embody high output power and high speed rotation. Still another purpose of the present invention is to provide a rotary engine comprising: a cylinder including an inlet port in one side and an outlet port in the other side; a rotor installed to a main shaft within the cylinder rotating eccentrically to the direction of the inner circumference of the cylinder; a vane operated by the rotor rotating within the cylinder to organize a compression chamber and a suction chamber within the rotor; and a crank material, rotated by the main shaft, including a crank arm in the end of the crank, and a cam installed to a crank shaft linked with the crank arm, wherein the vane corresponds to the rotor according to operations of the cam. In more, the crank material with a shape of "Y" , further comprises a supporting rod located at the one branch of the "Y' shape of the crank material, connecting the main shaft with the end portion; and two branch rods located at the remained two branches of the "Y" shape of the crank material, including the crank arm, the crank shaft linked with the crank arm, and the cam linked with the crank shaft, respectively, wherein the two vanes corresponds with the rotor according to operations of the cam. In more, the rotary engine further comprises a slider including a bearing material at both ends and at the top of each of the vanes corresponding to the cam to minimize friction between the cam and the vane. In more, the rotary engine further comprises a roller material at the slider sliding to the direction of a guide jaw of the cam to get closer adherence between the slider and the bearing material . In more, the rotary engine further comprises a turbine housing in the one side of the cylinder; a compressor housing in the one side of the cylinder isolated from the turbine housing; a turbine wheel installed at the main shaft penetrating the central axis of the turbine housing to receive a pressure of an outlet gas exhausted from the cylinder to enhance rotatory power of the main shaft; and a compressor wheel installed at the main shaft penetrating the central axis of the compressor housing to inhale and compress the external gas and to supply the compressed air with fuels to an inlet port of the cylinder forcedly. Still another purpose of the present invention is to provide a rotary engine comprising: a vane cavity in the one side of the inside of a cylinder; a vane at the vane cavity sliding into the outer circumference of the rotor, and rotating in a predetermined angle by a hinge of the one side; a compression surface forming concentric circle with a vane shaft not only to distribute high pressure of a fluid homogeneously but also to transfer compression force of the compression surface by the fluid to the vane shaft; a sealing means with a seal material installed to the end of the compression surface of the vane contacting with the rotor to maximize sealing states between the rotor and the vane; and a protuberance formed in the one side of the rotor, including a compression surface region in the one side of the protuberance, and a suction surface region in the other side of the protuberance, wherein the curvature of the compression surface region has slightly slower curvature than the suction surface region not only to prolong the compression time of the rotor, but also to increase compression force greatly according to the minimization of the compression chamber. In more, the rotary engine further comprises at least one seal groove formed at the proximity of the protuberance of the rotor, including a suspension groove at the inside to be sealed elastically by a seal and an elastic material; and at least one side seal groove formed at both edges of the rotor to be sealed elastically and sequentially by an elastic material, a rubber ring, and a side seal. In more, the sealing means further comprise a vane seal groove including a suspension groove at the end portion of the vane to install a spring and a vane seal material with a suspension jaw elastically; and a side seal groove connected with the vane seal groove and formed at the both sides of the compression surface of the vane to install a spring and a side seal elastically. In more, the rotary engine further comprises a seal fixation groove of a "L" shape at both sides of the vane seal groove of the vane, inserting and jointing a seal fixation material of a "L" shape to fix stably the vane seal material installed to the vane seal groove, and forming a shaft seal groove reaching to the portion of the vane shaft to install a spring and a shaft seal material elastically.

Brief Description of the Drawings

For a more complete understanding of the present invention and the advantages thereof, reference is now made to the following descriptions taken in conjunction with the accompanying drawings, in which like reference numerals denote like parts, and in which: Fig. 1 is a perspective view of the conventional rotary engine; Fig. 2 is a cross sectional view of the conventional rotary engine; Fig. 3 is a disassembled perspective view of a rotary engine according to a preferred embodiment of the present invention; Fig. 4 is a perspective view of a main part of the rotary engine according to a preferred embodiment of the present invention; Fig. 5 is a perspective view of the rotary engine according to a preferred embodiment of the present invention; Fig. 6a to Fig. 6d is a cross sectional view of the rotary engine according to a preferred embodiment of the present invention; Fig. 7 is a disassembled perspective view of the rotary engine according to other preferred embodiment of the present invention; Fig. 8 is a schematic cross sectional view of Fig. 7; Fig. 9 is a disassembled perspective view of the rotary engine according to another preferred embodiment of the present invention; Fig. 10 is a perspective view of Fig. 9; Fig. 11a to Fig. lid is a view of configuration of stroke procedures of the rotary engine according to the preferred embodiment of the present invention; Fig. 12a and Fig.12b are perspective views of a rotor selected from the rotary engine according to the preferred embodiment of the present invention; Fig. 13 is a perspective view of a vane selected from the rotary engine according to the preferred embodiment of the present invention; and Fig. 14a and Fig. 14b are examples of the vane selected from the rotary engine according to other preferred embodiment of the present invention.

Embodiment

Reference will now be made in detail to preferred embodiments of the present invention, example of which is illustrated in the accompanying drawings. Fig. 3 is a disassembled perspective view, Fig. 4 is a perspective view of a main part, Fig. 5 is a perspective view, and Fig. 6a to Fig. 6d is a cross sectional view of the rotary engine according to a preferred embodiment of the present invention. The rotary engine of the present invention comprises a cylinder 100 including an inlet port 110 in one side and an outlet port 120 in the other side, a rotor 200 at the main shaft S within the cylinder 100 rotating eccentrically following to the inner circumference of the cylinder 100, and a vane 300 operating with the rotation of the rotor 200 within the cylinder 100 to organize a compression chamber 310 and a suction chamber 320. As shown in Fig. 4 and Fig. 5, a crank material 400 of a "Y' shape rotates eccentrically to a crank SI of the main shaft S. The end of a supporting rod 410 at the bottom of the "Y' shape of the crank material 400 includes a shaft hole 411 connected with the main shaft S, and two branch rods 420 and 420" with the same length at the top of the "Y" shape of the crank material 400 includes crank shaft holes 421 and 42A, respectively. In more, crank shaft holes 421 and 42A corresponding to the branch rods 420 and 420" is connected with eccentric shafts 431 and 431" corresponding to eccentric arms 430 and 430", respectively. Additionally, the eccentric arms 430 and 430" include slightly longer crank shafts 440 and 440", respectively, and the crank shafts 440 and 440" includes cams 450 and 450" in a predetermined distance, respectively. Sequentially, the crank shafts 440 and 440" penetrates through cam holes of came cavities 140 and 140" placed at the top of vane cavities 130 and 130", respectively. Each of two vanes 300 installed at the vane cavities 130 and 130" of the cylinder 100 comprises a vane shaft 330, and the one side of the vane shaft 330 rotates in a predetermined angle in the corresponding vane cavities 130 and 130". The vane 300 comprises a compression surface 340 building up a concentric circle with the vane shaft 330 not only to distribute high pressure of the fluid homogeneously, but also to transfer the compression force of the compression surface 340 by the fluid again to the vane shaft 330 to avoid damage of the vane 300. As shown in Fig. 5, a fixation hollow 350 is formed at the top of the vane 300, and a slider 360 of cylindrical shape is fixed to the fixation hollow 350 by a bolt and so on. Each of both ends of the slider 360 includes a rotatable bearing material 360a making rotation of the corresponding cams 450 and 450" rotate easily, and the one side of the slider 360 includes a supporter 361 in a longitudinal direction. In more, each of both ends of the supporter 361 installs a roller material 362 sliding to the inner circumference of corresponding guide jaws 451 and 451" of the cams 450 and 450". Therefore, a gap between the cams 450 and 450" and the bearing material 360a is minimized to avoid operation noise. Additionally, a spring 363 installed between the vane

300 and the vane cavity 130 makes the vane 300 adhere closely to the cams 450 and 450" to minimize the gap between the cams 450 and 450" and the bearing material 360a to avoid any mechanical noise. In more, a sealing means 370 maintaining sealing states between the rotor 200 and the cylinder 100 is installed at the end of the compression surface 340 of the vane 300. As shown in Fig. 4, the sealing means 370 comprises a vane seal material 372 at a vane, seal groove

371 of the end of the vane 300 to maintain sealing states with the rotor 200, and a spring (not shown) installed between the vane seal groove 371 and the vane seal material

372 adheres the vane seal material 372 to the outer circumference of the rotor 200 closely at constant pressure. In more, a side seal groove 373 is formed to the direction of both sides of the compression surface 340 of the vane 300 and connected with the vane seal groove 371. Additionally, a side seal material 374 and a spring are installed sequentially. Therefore, the compressed air generated form the compression chamber 310 is not leaked into the vane cavity 130 of the cylinder 100. On the contrary, the cylinder 100 is protected by a housing (not shown) , and the number of the cylinder 100 in the inside of a housing would be more than 10. In this case, after installing the rotors 200 respectively, the rotors 200 are penetrated and jointed with the main shaft S to get a very large output. Fig. 7 is a disassembled perspective view of the rotary engine according to other preferred embodiment of the present invention. A turbine housing 500 with a side seal plate 550 and a compressor housing 600 with a side seal plate 650 are installed in one side of the cylinder 100, while the turbine housing 500 and the compressor housing 600 are isolated from each other. As shown in Fig. 8, a gas inlet port 510 formed at the one side of the turbine housing 500 is connected with the outlet port 120 of the cylinder 100 through the outlet duct 520, and a gas outlet port 530 is formed in the other side of the turbine housing 500. In more, the main shaft S penetrating the central axis of the turbine housing 500 includes a turbine wheel 540 receiving the pressure of the gas inhaled from the gas inlet port 510 and enhancing rotatory power of the main shaft S. In other words, the turbine wheel 540 is rotated by using the outlet gas exhausting to the outside. Therefore, the rotatory power of the main shaft S is further enhanced to increase efficiency and output of the rotary engine in operations of high speed. Additionally, a compressed air outlet 610 formed in the one side of the compressor housing 600 is connected with the inlet port 110 of the cylinder 100 through the supply duct 620, and an air inlet port 630 inhaling the external air from the outside is formed in the other side of the compressor housing 600. In more, the main shaft S penetrating the central axis of the compressor housing 600 includes a compressor wheel 640 supplying forcedly fuels with the compressed air inhaled through the air inlet port 630 to the inlet port 110 of the cylinder 100 Fig. 9 is a disassembled perspective view, and Fig. 10 is a perspective view of the rotary engine according to another preferred embodiment of the present invention. After the vane cavity 130 is formed deeply in the one side within the cylinder 100 to immense the vane 300 completely, the vane 300 of the vane cavity 130 sliding to the outer circumference of the rotor 200 rotates in a predetermined angle by the one side of the vane shaft 330. In more, the vane 300 comprises the compression surface 340 forming a concentric circle with the vane shaft 330 not only to distribute high pressure of the fluid homogeneously, but also to transfer the compression force of the compression surface 340 by the fluid again to the vane shaft 330. As shown in Fig. 11a to Fig. lid, after a protuberance 210 is formed in the one side of the rotor 200, a compression surface region 220 is formed in the one side of the protuberance 210 and a suction surface region 230 is formed in the other side of the protuberance 210. The compression surface region 220 has slightly slower curvature than the suction surface region 230 not only to prolong the compression time of the rotor 200, but also to increase the compression force greatly according to the minimization of the compression chamber 310. In other words, as shown in the graph below, the compression force of an engine, A in graph, using either a rotor or a piston is rapidly reduced at the peak of the compression, when the area of the compression surface region 220 is almost the same with the area of the suction surface region 230. On the contrary, when the curvature of the compression surface region 220 is slightly slower than that of the suction surface region 230 of the rotor 200, the compression force of an engine of the present invention, B in graph, is prolonged to a certain amount of time at the peak of the compression not only to keep the continuous output of high power, but also to increase greatly compression efficiency of the compression chamber 310.

Al ES As shown in Fig. 12a and Fig. 12b, after a seal groove 240 is formed in a predetermined interval in the inside of the proximity of the protuberance 210 of the rotor 200, a seal 243 and an elastic material 242, such as a spring, are installed elastically to the seal groove 240 to keep sealing states between the rotor 200 and the vane 300. In more, after two side seal grooves 244 are formed to the direction of the both edges of the rotor 200, a robber ring 247, a side seal 246, and an elastic material 245 are installed to the side seal groove 244 to keep sealing states between the rotor 200 and a housing site block (not shown) . A sealing means 350 is installed to the end of the compression surface 340 of the vane contacting with the rotor 200. As shown in Fig. 14, after the sealing means 350 forms a vane seal groove 351 comprising a suspension groove 351a in the end of the vane 300, a spring 353 and a vane seal material 352 with a suspension jaw 352a are installed to make the vane seal material 352 adhere closely to the outer circumference of the rotor 200 by constant pressure from the spring 353. In more, after a side seal groove 354 connected with the vane seal groove 351 is formed is formed to the direction of both edge of the compression surface 340 of the vane 300, a spring 355 and a side seal 357 is installed sequentially to prevent the compressed air generated at the compression chamber 310 from leaking to the vane cavity 130. As shown in Fig. 13, after each of seal fixation grooves 358 of a "L" shape is formed in both sides of the vane seal groove 351 of the vane 300, and after each of seal fixation materials 358a of a "L" shape is inserted and jointed to fix stably the corresponding vane seal material 352 installed to the inside of the vane seal groove 351 to the seal fixation groove 358, a shaft seal groove 359 rotating and reaching to a part of the vane shaft 330 is formed in the seal fixation groove 358, and a spring 359a and a shaft seal material 359b are installed to the shaft seal groove 359. On the contrary, as shown in Fig. 9, a cam 250 with a shape of an irregular end is installed to the side of the rotor 200, and the cam 250 comprises a locker arm 700 connected with the vane shaft 330 of the vane 300 to operate a control instrument (not shown) regulating the behavior of the vane 300. An inner and an outer circumference rollers 710 and 720 installed to the end of the locker arm 700 slide in the states of contacting to the inner and outer circumference of a guide 251 to prevent free motions of the locker arm 700 and the vane 300 connected to the locker arm 700. Effects of operations of the rotary engine described in the above statements will be explained in detail in the following statements. As shown in Fig. 5 and Fig. 6a to Fig. 6d, when the main shaft S is rotated by an external power, the crank si connected to the main shaft S is rotated to make the crank material 400 connected to the crank Si rotate eccentrically. At this moment, two branch rods 420 and 420" at the top of the crank material 400 makes the eccentric arms 430 and 430", the crank shaft 440 and 440" connected to the eccentric arms 430 and 430", and two cams 450 and 450" connected to the crank shaft 440 and 440" rotate eccentrically with a constant orbit. Simultaneously, the cams 450 and 450" rotates in the states of facing to the bearing material 360a installed to the both sides of the slider 360 of the vane 300, so that the vane 300 is sequentially contacted with or separated from the outer circumference of the rotor 200 rotating eccentrically to perform an exhaustion-suction-compression- expansion procedures sequentially, as shown in Fig. 6a to Fig. 6d. At this moment, the roller material 362 of the slider 360 connected to the vane 300 slides to the inner circumference of the corresponding guide jaws 451 and 451" of the cams 450 and 450", and the spring 363 installed between the vane 300 and the vane cavity 130 makes the vane 300 adhere closely to the cams 450 and 450" to minimize the gap between the cams 450 and 450" and the bearing material 360a to avoid any mechanical noise. On the contrary, two vanes 300 installed to the vane cavities 130 and 130" of the cylinder 100 comprises the compression surface forming a concentric circle with the vane shaft 330 not only to distribute high pressure of the fluid homogeneously, but also to transfer the compression force of the compression surface 340 by the fluid to the vane shaft 330, like the arrow mark shown in Fig. 6a to Fig. 6d, to prevent damage of the vane 300 due to high compression. The vane seal material 372 of the sealing means 370 is installed to the end of the compression surface 340 of the vane 300 to keep sealing states between the rotor 200 and the vane 300, and the side seal material 374 is installed elastically to the both sides of the compression surface 340 of the vane 300 to prevent the compressed air generated from the compression chamber 310 from leaking to the vane cavity 130 of the cylinder 100. On the contrary, the outlet gas from the cylinder 100 is exhausted through the outlet port 120 at the one side of the cylinder 100 as shown in Fig. 8. At this moment, the outlet gas is inhaled into the inside of the turbine housing 500 through the outlet duct 520 connected with the outlet port 120 to drive the turbine wheel 540 so that the rotatory power of the main shaft S is further enhanced to increase efficiency and output of the rotary engine in operations of high speed. Additionally, the outlet gas inhaled into the inside of the turbine housing 500 is exhausted into the outside through the gas outlet port 530. Simultaneously, when the main shaft S is rotated, the compressor wheel 640 installed to the main shaft S in the inside of the compressor housing 600 is also rotated in high speed. At this moment, the rotatory power of the compressor wheel 640 inhales the external air into the air inlet port 630 of the one side of the compressor housing 600, and compresses the inhaled air into high pressure. In more, the compressed air accompanying with fuels are supplied forcedly into the inlet port 110 of the cylinder 100 through the supply duct 620 On the contrary, as shown in Fig. 9 and Fig. 10, the vane cavity 130 of the cylinder 100 is deeply formed to immense the vane 300 completely to minimize the compression space while driving the rotor 200, and the vane 300 comprises the compression surface 340 forming concentric circle with the vane shaft 330 not only to distribute high pressure of the fluid to the compression surface 340 homogeneously, but also to transfer the high pressure of the fluid to the vane shaft 330 to prevent abrasion or damage of the vane 300. Additionally, to keep sealing states between the vane 300 and the rotor 200, a sealing means 350 is installed to the end of the compression surface 340 of the vane 300. As shown in Fig. 13a and Fig. 13b, numerous springs 353 are fixed to the vane seal groove 351 of the vane 300 at first, and the vane seal material 352 is installed elastically. In more, the suspension jaw 352a of the vane seal material 352 is jointed with the suspension groove 351a of the vane seal groove 351 not only to prevent deviation of the vane seal material 352 to the outside, but also to push up the vane seal material 352 to make the vane 300 adhere closely to the outer circumference of the rotor 200 at a constant pressure . Additionally, the spring 355 and the side seal 357 is installed sequentially to the side seal groove 354 at the both sides of the vane 300 to prevent the compressed air generated at the compression chamber 310 from leaking to the vane cavity 130. In more, as shown in Fig. 13a and Fig. 13b, after the seal fixation material 358a of a "L" shape is inserted and jointed to fix stably the vane seal material 352 installed to the inside of the vane seal groove 351 to the seal fixation groove 358 of the vane 300, the shaft seal groove 359 rotating a part of the vane shaft 330 is formed in the seal fixation groove 358, and the spring 359a and the shaft seal material 359b are installed to the shaft seal groove 359 to prevent the compressed air generated from the compression chamber 310 from leaking to the vane cavity 130 of the cylinder 100 perfectly. On the contrary, after the protuberance 210 is formed in the one side of the rotor 200, the compression surface region 220 is formed in the one side of the protuberance 210 and the suction surface region 230 is formed in the other side of the protuberance 210 not only to prolong compression time of the rotor 200, but also to increase greatly the compression force according to the minimization of the compression chamber 310. In more, after the seal groove 240 is installed to the proximity of the protuberance 210 of the rotor 200, the seal 243 and the elastic material 242 are installed elastically to the seal groove 240 to keep sealing states between the rotor 200 and the vane 300. On the contrary, the side seal 246, and the elastic material 245 are installed elastically to the side seal groove 244 at both sides of the rotor 200 to keep sealing states between the rotor 200 and the housing site block (not shown) . Finally, the cam 250 with a shape of the irregular end is formed to the side of the rotor 200, and the cam 250 comprises the locker arm 700 connected with the vane shaft 330 of the vane 300 to operate the control instrument (not shown) regulating the behavior of the vane 300. The inner and an outer circumference rollers 710 and 720 installed to the end of the locker arm 700 slide in the states of contacting to the inner and outer circumference of the guide 251 to prevent free motions of the locker arm 700 and the vane 300 connected to the locker arm 700. As described in the above statements, the rotary engine of the present invention driving the vane 300 by the crank material 400 linked with the main shaft S operates homogeneously to keep closely and constantly the gap between the rotor 200 and the vane 300 to maximize compression efficiency of the rotary engine, and the vane 300 is maintained at continuous homogeneous operations to prevent damage generated by weakening of the compression force of the vane 300. In more, the rotary engine of the present invention installs the turbine wheel 540 to the main shaft S rotated by high pressure of the outlet gas to increase rotatory power of the main shaft S, and the compressor wheel 640 to the man shaft S inhaling and compressing the external air to supply the compressed air with fuels to the inlet port 110 of the cylinder 100 not only to simplify the conventional mechanical complexity of using extra driving means to rotate the compressor wheel 640, but also to reducing the entire volume of the conventional rotary engine . In more, the rotary engine of the present invention distributes the compression force transferred to the vane 300 homogeneously to make the vane 300 slide smoothly with the rotor 200, installs elastically the sealing means 350 keeping the sealing states between the vane 300 and the rotor 200 not only to prolong the lifespan of the rotary engine, but also to lower pulsation generated by pressure difference between the suction chamber and the compression chamber, and improves a shape of the rotor 200 not only to inhale enough amount of air, but also to exert high compression force to provide the rotary engine of high output power (difficult in embodying such rotary engine in the past) and high speed rotation. While the invention has been particularly shown and described with reference to preferred embodiments thereof, it will be understood by those skilled in the art that the foregoing and other changes in form and details may be made therein without departing from the spirit and scope of the invention.

Claims

What is claimed is :

1. A rotary engine comprising: a cylinder including an inlet port in one side and an outlet port in the other side; a rotor installed to a main shaft within the cylinder rotating eccentrically to the direction of the inner circumference of the cylinder; a vane operated by the rotor rotating within the cylinder to organize a compression chamber and a suction chamber within the rotor; and a crank material, rotated by the main shaft, including a crank arm in the end of the crank, and a cam installed to a crank shaft linked with the crank arm, wherein the vane corresponds to the rotor according to operations of the cam.

2. The rotary engine according to claim 1, wherein the crank material with a shape of "Y" , further comprising: a supporting rod located at the one branch of the "Y' shape of the crank material, connecting the main shaft with the end portion; and two branch rods located at the remained two branches of the ^Λ,Y" shape of the crank material, including the crank arm, the crank shaft linked with the crank arm, and the cam linked with the crank shaft, respectively, wherein the two vanes corresponds with the rotor according to operations of the cam.

3. The rotary engine according to claim 2 , further comprising a slider including a bearing material at both ends and at the top of each of the vanes corresponding to the cam to minimize friction between the cam and the vane.

4. The rotary engine according to claim 3 , further comprising a roller material at the slider sliding to the direction of a guide jaw of the cam to get closer adherence between the slider and the bearing material .

5. The rotary engine according to claim 1, further comprising: a turbine housing in the one side of the cylinder; a compressor housing in the one side of the cylinder isolated from the turbine housing; a turbine wheel installed at the main shaft penetrating the central axis of the turbine housing to receive a pressure of an outlet gas exhausted from the cylinder to enhance rotatory power of the main shaft; and a compressor wheel installed at the main shaft penetrating the central axis of the compressor housing to inhale and compress the external gas and to supply the compressed air with fuels to an inlet port of the cylinder forcedly.

6. A rotary engine comprising: a vane cavity in the one side of the inside of a cylinder; a vane at the vane cavity sliding into the outer circumference of the rotor, and rotating in a predetermined angle by a hinge of the one side; a compression surface forming concentric circle with a vane shaft not only to distribute high pressure of a fluid homogeneously but also to transfer compression force of the compression surface by the fluid to the vane shaft; a sealing means with a seal material installed to the end of the compression surface of the vane contacting with the rotor to maximize sealing states between the rotor and the vane; and a protuberance formed in the one side of the rotor, including a compression surface region in the one side of the protuberance, and a suction surface region in the other side of the protuberance, wherein: the curvature of the compression surface region has slightly slower curvature than the suction surface region not only to prolong the compression time of the rotor, but also to increase compression force greatly according to the minimization of the compression chamber.

7. The rotary engine according to claim 6, further comprising: at least one seal groove formed at the proximity of the protuberance of the rotor, including a suspension groove at the inside to be sealed elastically by a seal and an elastic material; and at least one side seal groove formed at both edges of the rotor to be sealed elastically and sequentially by an elastic material, a rubber ring, and a side seal.

8. The rotary engine according to claim 6 , wherein the sealing means further comprise: a vane seal groove including a suspension groove at the end portion of the vane to install a spring and a vane seal material with a suspension jaw elastically; and a side seal groove connected with the vane seal groove and formed at the both sides of the compression surface of the vane to install a spring and a side seal elastically.

9. The rotary engine according to claim 8 , further comprising a seal fixation groove of a "L" shape at both sides of the vane seal groove of the vane, inserting and jointing a seal fixation material of a "L" shape to fix stably the vane seal material installed to the vane seal groove, and forming a shaft seal groove reaching to the portion of the vane shaft to install a spring and a shaft seal material elastically.