WO2014005262A1

WO2014005262A1 - Rotary engine

Info

Publication number: WO2014005262A1
Application number: PCT/CN2012/078038
Authority: WO
Inventors: 邱奕恭
Original assignee: Chiu Yi-Kung
Priority date: 2012-07-02
Filing date: 2012-07-02
Publication date: 2014-01-09

Abstract

A rotary internal combustion engine, comprising an internal transmission shaft (28), an intermediate transmission shaft (26), an external transmission shaft (24), three pairs of pistons (241-256), a first elliptical gear (32), a second elliptical gear (33), a third elliptical gear (35), and a fourth elliptical gear (36). The internal transmission shaft (28), the intermediate transmission shaft (26) and the external transmission shaft (24) overlap each other, and are respectively and fixedly connected to a corresponding pair of pistons; each pair of pistons are interleaved and symmetrically disposed; the first elliptical gear (32) is fixedly connected to the external transmission shaft (24); the internal transmission shaft (28) and the intermediate transmission shaft (26) respectively have an oblique spline (282, 262) at different angles, and are connected to the second elliptical gear (33) via equal oblique spline; the third elliptical gear (35) and the fourth elliptical gear (36) perpendicularly intersect with each other, and are fixedly connected to a power output shaft (34); the first elliptical gear (32) is engaged with the fourth elliptical gear (36); and the second elliptical gear (33) is engaged with the third elliptical gear (35). The rotary engine can effectively utilize the usable space of a cylinder, and has a simple structure and variable compression ratios.

Description

Rotating engine

Technical field

The present invention relates to a rotary engine, and more particularly to a rotary guide that simplifies structure and increases performance

Background technique

Please refer to Figure 1, which includes states la to ld, which are schematic diagrams of the working principle of a reciprocating piston in a conventional reciprocating piston engine. The principle of engine operation is through the process of converting the energy produced by burning fuel into mechanical kinetic energy.

As in the state la, the fuel 101 is fed into the cylinder 1 via the intake port 11, and then, as in the state lb, the fuel 101 in the cylinder 1 is compressed. Thereafter, as in the state lc, after the compressed fuel 101 is ignited by the pilot unit 13, the fuel 101 is instantaneously burned and exploded into a gas 102, and an output power is generated by the volume expansion to push the piston 15. The output power generated by the explosion converts the linear motion of the piston 15 into the rotational motion of the crankshaft 14. Gas 102 is combusted and converted to exhaust gas 103, which is vented via venting port 12 (e.g., state ld). Thereafter, the above-described inhalation, compression, explosion, and exhaust strokes are repeated to convert the power output generated by the linearly moving piston 15 into the rotational motion of the crankshaft 14.

However, since the conventional cylinder 1 can only perform the four-stroke operation with a piston 15, that is, the stroke of up and down reciprocation, when the piston 15 is at the top dead center 151 or the bottom dead center 152 of the stroke, the piston 15 is The space available in the cylinder 1 will be greatly reduced, that is, the engine using such a reciprocating piston cannot effectively utilize all the space in the cylinder 1. Moreover, because of the movement relationship between the piston rod and the crank shaft 14, the piston 15 generates a great friction force when the cylinder 1 is operated, thereby reducing the efficiency of the conventional engine.

In addition, the compression ratio of the conventional engine is usually fixed. Take the Otto cycle engine, which is a heat engine cycle commonly used in car engines. This type of engine needs to work with a spark plug, and most of its fuel is gasoline. According to the theoretical thermal efficiency = 1-Λ, the theoretical thermal efficiency is related to the compression ratio r of the engine and the heat capacity ratio γ of the gas in the combustion chamber. When the heat capacity ratio is fixed by γ and the compression ratio is higher, according to the above formula, the thermal efficiency of the engine is also higher. However, when the engine is running at different speeds, the efficiency of the intake air is different because of the different efficiency of the intake air. Sometimes the intake efficiency is poor. When the compression of the engine is designed to be fixed, the efficiency of the intake air is different. So the actual compression ratio will not be the same. When the compression ratio is too high, the oil and gas mixture will cause knocking due to high temperature and high pressure premature spontaneous combustion before the spark plug is ignited, thus causing engine damage. For a conventional engine with a fixed compression ratio, in order to avoid knocking problems, The compression ratio of the engine is designed to be the best in terms of intake efficiency and does not produce a knock ratio. The problem is that, in general, the engine is not necessarily in the case of the best intake efficiency, and the general known engine is not in the case of the best intake efficiency, and its thermal efficiency is actually poor. In other words, it is more energy-intensive.

Therefore, it has become one of the important topics to provide an engine that can effectively utilize the cylinder's use space, has a simple structure, a small size, a small number of parts, and can change the compression ratio to achieve a high energy consumption and high power. Summary of the invention

In view of the above problems, an object of the present invention is to provide a rotary engine that can effectively utilize the use space of an engine cylinder, simplify an engine structure, and can change a compression ratio to achieve power and reduce energy consumption.

To achieve the above object, a rotary engine according to the present invention includes an inner drive shaft, a middle drive shaft, an outer drive shaft, three pairs of pistons, a first elliptical gear, a second elliptical gear, and a third ellipse. Gear with a fourth elliptical gear. Wherein, the inner drive shaft, the middle drive shaft and the outer drive shaft are nested with each other, and the inner drive shaft, the middle drive shaft and the outer drive shaft are respectively fixed with a corresponding pair of pistons, and each pair of pistons is staggered and symmetrically arranged. The first elliptical gear is fixed to the outer drive shaft, and the inner drive shaft and the middle drive shaft respectively have a diagonal bolt slot at different angles, and are connected to the second elliptical gear by the equal oblique bolt slot. The third elliptical gear intersects the fourth elliptical gear perpendicularly and is fixed to a power output shaft, the first elliptical gear meshes with the fourth elliptical gear, and the second elliptical gear meshes with the third elliptical gear.

In an embodiment of the present invention, the rotary engine further includes: a gear box body, an annular cylinder block, the gear box body has an accommodating space, and the annular cylinder block is disposed outside the accommodating space of the gear box body, and includes a first a shaft hole, a second shaft hole and an accommodating space, the inner drive shaft has a two-axis body, wherein one shaft shaft is disposed on the first shaft hole of the annular cylinder block, and the other shaft body is disposed in the second shaft hole The middle transmission shaft has a shaft hole and a hollow shaft body, and the shaft body of the inner transmission shaft penetrating the second shaft hole is bored through the shaft hole of the middle transmission shaft, and the transmission shaft has a shaft hole and a hollow shaft The hollow shaft body portion of the middle transmission shaft is disposed through the shaft hole of the outer transmission shaft, and the shaft body portion of the inner transmission shaft passes through the hollow shaft body and penetrates through the second shaft hole of the annular cylinder block to partially protrude Ring cylinder,

a plug, a fourth piston, a fifth piston and a sixth piston, in the accommodating space of the cylinder block and fixed to the outer drive shaft, and the third piston and the fourth piston are disposed on the annular cylinder block The fifth elliptical gear is disposed in the accommodating space of the annular cylinder block and is fixed to the inner transmission shaft, and the first elliptical gear has a gear portion, and the first elliptical gear is fixed in the accommodating space. The utility model is disposed in the accommodating space of the gear box body, and is connected to the shaft body of the outer transmission shaft portion protruding from the annular cylinder block, The second elliptical gear has a gear portion, and the second elliptical gear is disposed in the accommodating space of the gear box, and is connected with the central transmission shaft and the shaft body of the inner transmission shaft portion protruding from the annular cylinder block, and the third elliptical gear is disposed. a gear portion of the gear unit, the gear portion of the third elliptical gear meshes with the gear portion of the second elliptical gear, and the fourth elliptical gear is disposed in the accommodating space of the gear box. The gear portion, the gear portion of the fourth elliptical gear meshes with the gear portion of the first elliptical gear, and the power output shaft is pivotally mounted to the gear housing.

In an embodiment of the invention, the annular cylinder block is an annular hollow cylinder composed of two semi-annular cylinder blocks, and the annular cylinder block is provided with an air inlet, an exhaust port and one or more pilot ports.

In an embodiment of the invention, the annular cylinder block is provided with more than one fuel injection port.

In an embodiment of the invention, each piston is disposed in the annular cylinder body sequentially, and has a space between the two, respectively, and the space respectively forms an air suction portion, a compression portion, an explosion portion, an exhaust portion and two adjustments. unit.

In an embodiment of the invention, the first piston, the second piston, the third piston, the fourth piston, the fifth piston and the sixth piston respectively have two piston faces, and the piston faces of the first piston and the second piston are respectively A half-type combustion chamber is provided, and the third piston, the fourth piston, the fifth piston and the sixth piston are provided with a half-type combustion chamber only for the piston faces facing the first piston and the second piston.

In an embodiment of the invention, the air inlet and the adjacent two piston surfaces of the semi-type combustion chamber form an intake portion, and the exhaust port forms an exhaust gas with two piston surfaces adjacent to the semi-type combustion chamber. a pilot portion forms an explosion portion with two piston faces adjacent to the semi-type combustion chamber, a compression portion is formed between the two pistons between the intake port and the pilot port, and the pistons of the two pistons face the intake port The surface has a semi-combustion chamber, the adjustment portion is formed by a space formed between the two pistons, and the semi-type combustion chamber is not disposed on the piston surface facing the adjustment portion.

In an embodiment of the present invention, a hollow plug is disposed on a piston surface facing the adjusting portion, the hollow plug is arc-shaped, and the center of the arc is the same as the axis of each transmission shaft in the plane of the arc, and the hollow plug has a plug surface. The embolization mask has a hole for circulating liquid, and the other piston surface is provided with a plug cylinder, the plug cylinder is arc-shaped, and the arc-shaped center is coaxial with the axis of each drive shaft in the plane of the arc to accommodate the hollow plug, the inside of the plug cylinder Can accommodate circulating liquids.

In an embodiment of the present invention, at least one first cooling liquid flow pipe is disposed on a piston surface facing the adjusting portion, and the first cooling liquid flow pipe is formed in an arc shape, and the arc-shaped center of the arc is in the arc-shaped plane of each of the transmission shaft axes. The first cooling liquid flow pipe communicates with a sealed space in the piston, and the other piston surface is provided with at least one second cooling liquid flow pipe, and the second cooling liquid flow pipe is arc-shaped, and the arc-shaped circular center has the arc-shaped plane of each transmission shaft The axial center, and the inner diameter of the second cooling liquid flow pipe is matched with the outer diameter of the first cooling liquid flow pipe, and the piston is connected to the inner drive shaft, the middle drive shaft and the bottom of the outer drive shaft respectively. a cooling liquid circulation port, and respectively communicating with the first cooling liquid flow pipe and the second cooling liquid flow pipe, wherein the inner transmission shaft and the corresponding piston connection portion are respectively provided with at least one cooling liquid flow port, respectively, and the inner transmission shaft shaft Another cooling liquid flow port of the core is connected, wherein the cooling liquid flow ports communicate with each other when the fifth piston is engaged with the inner transmission shaft.

In an embodiment of the invention, the second elliptical gear that pushes the inner transmission shaft and the oblique bolt slot of the middle transmission shaft is moved on the rotation axis to make the inner transmission shaft and the middle transmission shaft of the second elliptical gear connected The rotation of different angles causes the corresponding pistons fixed to the inner transmission shaft and the middle transmission shaft to expand or become smaller.

The rotating engine of the present invention utilizes the characteristic of the elliptical gear transmission ratio to periodically change, controls the three sets of pistons for variable-speed rotation, and generates suction, pressure, and suction through the intake duct, the mixed gas ignition device and the exhaust duct provided by the annular cylinder block. The explosion and the row are actuated, and the power output shaft is rotated at the same time, and the rotational energy is output.

Since there is no complicated valve mechanism and crankcase arrangement of the conventional engine, the volume of the rotary engine of the present invention is greatly reduced. At the same time, the rotary engine is running in the whole process in a rotating manner, and it can run very smoothly, which greatly reduces the situation in which the known engine pistons vibrate in a straight line and in a complex operation. Moreover, the piston of the rotary engine is directly fixed to the transmission shaft, and there is no known engine piston running to the explosion stroke, which generates a large lateral force to promote the significant friction loss of the cylinder wall, thereby improving the performance of the operation.

In addition, the present invention utilizes a compression ratio increase/decrease pusher to axially slide an elliptical gear that is slotted in the inclined pin slots of the two transmission shafts at an angle of positive and negative, so that the slot is connected thereto. The angle between the two pairs of pistons on the two transmission shafts increases the angle increase and decrease, and the compression ratio of the rotary engine can be changed when the rotary engine performs the compression stroke. In this way, the rotating engine can be given different compression ratios under different intake efficiency, different working temperatures, different internal and external conditions, so that each drop of fuel can be utilized to the maximum extent, thereby improving the rotating engine. The thermal efficiency, which in turn enables a powerful, energy-efficient rotary engine. DRAWINGS

1 is a schematic view showing a state of operation of a reciprocating piston of a conventional reciprocating piston engine;

2A is an exploded exploded view of the rotary engine of the present invention;

2B is a perspective view of the annular cylinder block in the rotary engine of the present invention;

3A and 3B are schematic views showing the meshing of the circular gear of the elliptical rotating engine of the present invention;

4A, 5 to 8 are front views of some components of the rotary engine of the present invention;

4B and 9 are perspective views of a part of the components of the rotary engine of the present invention. [Main component symbol description]

1: cylinder la~ld: state

101: Fuel 102: Gas

103: Exhaust gas 11: intake hole

12: Vent hole 13: Pilot unit

14: Crankshaft 15:

151: Top dead center 152: Bottom dead point

2: Rotating engine 21: gear housing

211, 212, 214, 215, 241, 261, 291: Shaft hole

213: accommodating space 216: sliding axis

217, 2544: Hole 22: Inner annular cylinder block

221, 231: Air inlet 223: Second shaft hole

224, 225, 236, 245, 246, 2514 2515, 2554, 281, 285, 287: Coolant flow port

227, 228: Cooling liquid flow channel 23: Outer annular cylinder block

232: Exhaust port 233: First shaft hole

234: Annular cylinder block 235: Pilot port

24: Outer drive shaft 242: Serrated groove

243, 263: hollow shaft body 244, 264, 284: groove

251: first piston 252: second piston

2511, 2521, 2531, 2541, 2551, 2561: convex birch

2512: Half-type combustion chamber

2513, 2523, 2532, 2542, 2552, 2562: Piston ring groove

2516: First piston ring 253: Third piston

2534: Second piston ring 254: Fourth piston

255: fifth piston 256: sixth piston

2535, 2545, 2555, 2565: Cooling night flow tube

2543: Hollow embolism of the cushioning mechanism

2553: Buffer cylinder for buffer mechanism

26: Middle drive shaft 262, 282: inclined bolt groove

28: Inner drive shaft 29: Outer annular cylinder cover 283, 286: Axle body

30: Half bearing

31: Compression ratio increase and decrease gear holder

312, 392: Screw holes 313, 393: Slide shaft holes

32: first oval gear

321, 351: hub groove

322, 332, 352, 362: gear section

33: second oval gear 333: annular flange

34: PTO shaft 35: Third elliptical gear

36: Fourth elliptical gear 38: Compression ratio increase and decrease pusher

381: Pushing the shaft

39: Compression ratio increase and decrease gear holder

391: Rotating accommodation space 40: Pilot unit

Al~a4: long side bl~b4: short side

Ω1~ω4: angular velocity

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Hereinafter, a rotary engine of a preferred embodiment of the present invention will be described with reference to the accompanying drawings, wherein like elements will be described with the same reference numerals.

Please refer to FIG. 2A and FIG. 2B, which are exploded exploded views of a rotary engine 2 according to an embodiment of the present invention. The rotary engine 2 includes a gear housing 21, an inner annular cylinder block 22, an outer annular cylinder block 23, an outer drive shaft 24, a first piston 251, a second piston 252, a third piston 253, and a first Four piston 254, a fifth piston 255, a sixth piston 256, six first type piston rings 2516, four second type piston rings 2534, a middle drive shaft 26, an inner drive shaft 28, and an outer annular cylinder a cover plate 29, a two-half type bearing 30, a compression ratio increase/decrease gear mount cover 31, a first elliptical gear 32, a second elliptical gear 33, a power output shaft 34, a third elliptical gear 35, A fourth elliptical gear 36, a second compression ratio increase/decrease pusher 38, a compression ratio increase/decrease gear mount 39, and two pilot devices 40.

In this embodiment, the gear housing 21 has an accommodating space 213 and two shaft holes 211 and 212, and an inner annular cylinder block 22 is disposed outside the shaft hole 211, and a second shaft hole 223 is disposed therebetween. There are half of the air inlet 221 and the exhaust port (not shown). The outer annular cylinder block 23 is symmetrically and closely connected to the other side of the inner annular cylinder block 22. The inner and outer annular cylinder blocks 22, 23 form an annular cylinder block 234, and also form an air inlet 231 and an exhaust port 232. . The center of the outer annular cylinder block 23 is provided with a first shaft hole 233, and the ring The cylinder block 234 is provided with one or more pilot ports 235 on the other side of the intake port 231. The outer annular cylinder cover plate 29 is disposed and closely attached to the outer side of the outer annular cylinder block 23, and is provided with a shaft hole 291 at the center.

Further, the inner transmission shaft 28 has two shaft bodies 283, 286, two groove portions 284 facing 180 degrees, and a diagonal bolt groove portion 282. The shaft of the inner transmission shaft 28 is provided with a cooling liquid flow port 281, and each of the groove portions 284 is provided with two cooling liquid flow ports 285. The shaft body 286 is disposed on the first shaft hole 233 of the outer annular cylinder block 23 and passes through the shaft hole 291 of the outer annular cylinder cover 29. The shaft body 283 is disposed through the second shaft hole 223 of the inner annular cylinder block 22 and is axially disposed on the shaft hole 212 of the gear case body 21. The two groove portions 284 are disposed on the shaft body 283 in the annular cylinder block 234. The skew pin groove portion 282 is provided on the shaft body 283 in the gear case body 21.

Further, the middle transmission shaft 26 has a shaft hole 261, a diagonal bolt groove portion 262, a hollow shaft body 263, and two groove portions 264 which are adjacent to each other by 180 degrees. The diagonal pin groove portion 262 is provided on the hollow shaft body 263 in the gear case body 21. The two groove portions 264 are disposed on the hollow shaft body 263 in the annular cylinder block 234.

The shaft body 283 of the inner transmission shaft 28 is bored in the shaft hole 261, and the oblique bolt groove portion 282 protrudes from the oblique bolt groove portion 262. Both the oblique pin groove portion 282 and the oblique pin groove portion 262 are grooved in the axial center, and are inclined at the same angle and a certain angle.

Further, the outer drive shaft 24 has a shaft hole 241, a sawtooth groove portion 242, a hollow shaft body 243, and two groove portions 244 adjacent to each other at 180 degrees. The serration groove portion 242 is disposed on the hollow shaft body 243 protruding from the annular cylinder block 234. The two groove portions 244 are disposed on the hollow shaft body 243 in the annular cylinder block 234. The hollow shaft body 263 of the middle transmission shaft 26 is partially passed through the shaft hole 241, and the oblique bolt groove portion 262 protrudes from the sawtooth groove portion 242. In other words, in the accommodation space 213 of the gear case 21, the serration groove portion 242, the oblique pin groove portion 262, and the oblique pin groove portion 282 are provided from the shaft hole 211 to the shaft hole 212, respectively.

In addition, the diagonal pin groove portion 282, the oblique pin groove portion 262, and the sawtooth groove portion 242 are for illustrative purposes, and the present invention is not limited thereto.

In addition, the first piston 251, the second piston 252, the third piston 253, the fourth piston 254, the fifth piston 255, and the sixth piston 256 are alternately disposed in the annular cylinder block 234 and have a convex birch portion 2511, 2521, respectively. 2531, 2541, 2551, 2561. The birch portions 2551 and 2561 are respectively connected to the two groove portions 284 of the inner transmission shaft 28; the birch portions 2531 and 2541 are respectively connected to the two groove portions 264 of the middle transmission shaft 26, and the convex birch portion 2511. 2521 is respectively connected to the two groove portions 244 of the outer drive shaft 24. Furthermore, the piston faces of the first piston 251 and the second piston 252 are each provided with a half-type combustion chamber 2512, and the remaining pistons only face the piston faces of the first piston 251 and the second piston 252, and a semi-combustion chamber is provided. 2512. In other words, the present invention, by the combination described above, causes the two piston faces having the semi-type combustion chamber 2512 to form a working space for suction, pressure, explosion, and discharge, and simultaneously form four working spaces. However, for the piston face without the half-type combustion chamber 2512, an adjustment portion is formed to facilitate the compression ratio increase/decrease control mechanism 3 (detailed Ming) In operation, the rotation ratio of the rotary engine 2 of the present invention is adjusted, and the space does not have the functions of suction, pressure, explosion, and displacement.

The annular cylinder block 234 of the present embodiment has been previously described to include an intake port 231, an exhaust port 232, and a pilot port 235 that respectively connect the intake portion, the exhaust portion, and the explosion portion formed by the rotary engine 2 during operation. And a compression section.

Here, the suction portion is a space formed between the intake port 231 and two adjacent pistons having a piston face of the semi-combustion chamber 2512; the exhaust portion is an exhaust port 232 and the adjacent two have a semi-type combustion chamber a space formed between the pistons of the piston surface of the 2512; the explosion portion is a space formed between the pilot port 235 and two adjacent pistons having a piston face of the semi-combustion chamber 2512; and the compression portion is interposed between the air inlet 231 and A space formed between the two pilot ports 235 having piston faces of the semi-combustion chamber 2512. Wherein, the suction portion is for sucking in fuel or pure air, and the compression portion is for compressing the fuel mixture or pure air. After the compressed fuel mixture gas enters the explosion portion, the ignition device 40 that connects the ignition port 235 of the explosion portion is connected. The compressed fuel mixture is ignited, or in other embodiments, a fuel injection device (not shown in Fig. 2A) may be further disposed at the pilot port 235 to inject fuel into the gas of the compression portion. The fuel mixture is combusted, or is blasted by the pilot device 40 to create an explosive thrust that pushes the piston. The gas generated after the explosive portion burns the fuel mixture is removed through the exhaust port 232. The intake portion, the compression portion, the explosion portion, and the exhaust portion are four spaces sequentially formed in the annular cylinder block 234.

For example, when the inhalation operation is performed between the first piston 251, the sixth piston 256, and the air inlet 231, the space formed by the three is an air suction portion; or when the second piston 252, the fourth piston When the suction between the piston 254 and the intake port 231 is performed, the space formed between the three is an intake portion; when the first piston 251, the sixth piston 256 and the pilot port 235 are guided When the fuel is actuated, the space formed by the three is an explosion portion; or, when the pilot fuel is actuated between the second piston 252, the fourth piston 254 and the pilot port 235, the three The space formed between the two is the explosion, and so on.

When the rotary engine 2 is actually operated, it is activated via a switch, and the pilot device 40 (for example, a spark plug) ignites fuel (such as gasoline or diesel) pre-set in the explosion portion, and the explosion thrust generated by burning the fuel pushes the piston. After the rotary engine 2 is operated, the fuel is input from the intake port 231, or a fuel injection device (not shown in FIG. 2A) is disposed in the vicinity of the pilot device 40, and is injected into the annular cylinder block 234, and the above is repeated. Intake, compression, explosion, and exhaust strokes.

In addition, the first elliptical gear 32, the second elliptical gear 33, the third elliptical gear 35, and the fourth elliptical gear 36 are disposed in the accommodating space 213 of the gear housing 21, wherein the third elliptical gear 35 and the fourth elliptical gear 36 The phase difference is 90 degrees, and the elliptical gears 32, 33, 35, 36 respectively have a gear portion 322, 332, 352, 362, and the first elliptical gear 32 and the third elliptical gear 35 also have a hub groove portion 321, 351, respectively. , The fourth elliptical gear 36 also has a hub groove portion, but is not shown in the drawings. The hub groove portion 321 of the first elliptical gear 32 is grooved to the serration groove portion 242 of the outer drive shaft 24. The second elliptical gear 33 has an oblique hub groove portion 331 that engages with the oblique pin groove portion 282 and an oblique hub groove portion (not shown) that engages with the oblique pin groove portion 262, and at the same time, the oblique hub The groove portion 331 is grooved to the diagonal pin groove portion 282, and the oblique hub groove portion (not shown) is grooved to the oblique pin groove portion 262. The power output shaft 34 is pivotally disposed on the two shaft holes 214 and 215 of the gear case 21, and the hub groove portion 351 of the third elliptical gear 35 and the hub groove portion of the fourth elliptical gear 36 (not shown) are respectively staggered. The 90 degree slot is connected to the power output shaft 34. The gear portions 352 and 362 of the third elliptical gear 35 and the fourth elliptical gear 36 mesh with the gear portions 332 and 322 of the second elliptical gear 33 and the first elliptical gear 32, respectively.

Since the first piston 251 is disposed on the outer drive shaft 24, when the first piston 251 rotates, the outer drive shaft 24 will rotate accordingly, and at the same time, the first elliptical gear 32 fixed to the outer drive shaft 24 will be rotated. Further, the second piston 252 is disposed on the outer drive shaft 24 with respect to the first piston 251, so that when the first piston 251 is rotated, the second piston 252 is also rotated relative to the first piston 251. The same effect is obtained when the second piston 252 is interchanged with the first piston 251.

In addition, since the third piston 253 is disposed on the middle transmission shaft 26, when the third piston 253 rotates, the middle transmission shaft 26 will rotate accordingly, and at the same time, the second elliptical gear 33 that is grooved to the middle transmission shaft 26 is driven. Turn. Further, the fourth piston 254 is disposed on the middle transmission shaft 26 with respect to the third piston 253, so that when the third piston 253 is rotated, the fourth piston 254 is also rotated relative to the third piston 253. Further, since the inner transmission shaft 28 is slotted to the second elliptical gear 33, when the third piston 253 drives the second elliptical gear 33 to rotate, the inner transmission shaft 28 is also driven to rotate at the same time. In addition, the fifth piston 255 and the sixth piston 256 are fixed to the inner transmission shaft 28, so that when the third piston 253 rotates, the fifth piston 255 and the sixth piston 256 are also rotated. When the third piston 253, the fourth piston 254, the fifth piston 255, and the sixth piston 256 are interchanged, the same effect is obtained.

In addition, when the third piston 253 drives the middle transmission shaft 26 to rotate to drive the second elliptical gear 33 to rotate, the inner transmission shaft 28 is simultaneously rotated, thereby rotating the fifth piston 255 and the sixth piston 256 fixed to the inner transmission shaft 28. When the force transmission process is long, the transmission shaft itself has elasticity and the piston has inertia and its own force relationship, which causes the fifth piston 255 and the sixth piston 256 to operate, and generates a front-back vibration phenomenon around the rotation axis. In order to avoid this problem, the fourth piston 254 and the sixth piston 256 of the rotary engine 2 of the present invention are not provided with a piston face of the half-type combustion chamber 2512, and a hollow plug 2543 of a buffer mechanism is additionally provided, and the plug body is curved and curved. The center of the circle is the same as the axis of each drive shaft in the plane of the arc. The embedding mask has a hole 2544 for circulating liquid. The plug body is provided with a 0-ring for sealing the plug, so as to avoid internal liquid when the plug slides. leak. The third piston 253 and the fifth piston 255 are not provided with a piston surface of the half-type combustion chamber 2512, and each of the plug cylinders 2553 provided with a buffer mechanism for receiving the hollow plug 2543 of the buffer mechanism, the plug The cylinder body is also curved, and the center of the arc is the same as the axis of each of the transmission shafts in the plane of the arc, and the inside also accommodates the circulating liquid. Through the operation of the buffer mechanism, when the fourth piston 254 is instantaneously subjected to the force, since the circulating liquid itself has viscosity and cannot pass through the hole 2544 in real time, the force instantaneously received by the fourth piston 254 is mostly directly transmitted to the sixth piston. 256, and greatly reduce the vibration phenomenon of the transmission process. When the third piston 253, the fourth piston 254, the fifth piston 255, and the sixth piston 256 are interchanged, the same effect is obtained.

It should also be noted that the driving described in the specification is not intended to define the master-slave relationship of its actions, but to explain the connection relationship of its actions.

As described above, since the rotary engine 2 of the present invention connects the outer rotating shaft 24, the middle transmission shaft 26, and the six pistons 251, 252, 253 of the inner transmission shaft 28 through the four elliptical gears 32, 33, 35, 36, 254, 255, 256, the power generated by the strokes of the intake, compression, explosion, and exhaust in the annular cylinder block 234 is output to the power output shaft 34 and is output in a rotational manner. Therefore, the meshing connection relationship between the respective elliptical gears of the present invention will be described below in a schematic view. However, in order to clearly describe the change in the size of the suction portion, the compression portion, the explosion portion, and the exhaust portion in the space of the annular cylinder block 234, the following embodiment describes the space size by way of example. Wherein, the position of the suction portion in the annular cylinder block 234 is relative to the explosion portion, and the position of the compression portion in the annular cylinder block 234 is relative to the exhaust portion, and the strokes of suction, compression, explosion, and exhaust are simultaneously In each department.

3A and 3B are schematic views showing the meshing of the first elliptical gear 32, the second elliptical gear 33, the third elliptical gear 35, and the fourth elliptical gear 36 of the present invention. It should be noted that, for clarity of description, the meshing relationship between the first elliptical gear 32 and the fourth elliptical gear 36 is shown in FIG. 3A, and the meshing relationship between the second elliptical gear 33 and the third elliptical gear 35 is shown in the figure. 3B, but actually, from the connection relationship of FIG. 2A and the above, since the first elliptical gear 32 is disposed on the outer drive shaft 24, the second elliptical gear 33 is disposed on the middle drive shaft 26 and the inner drive shaft 28, respectively. The third elliptical gear 35 and the fourth elliptical gear 36 are disposed on the power output shaft 34. Therefore, when the first elliptical gear 32 drives the fourth elliptical gear 36, the rotation of the fourth elliptical gear 36 simultaneously drives the power output shaft 34 and the third elliptical gear 35 to rotate, and the rotation of the third elliptical gear 35 drives the second oval gear. 33 turns. Alternatively, when the second elliptical gear 33 drives the third elliptical gear 35, the rotation of the third elliptical gear 35 simultaneously drives the power output shaft 34 and the fourth elliptical gear 36 to rotate, and the rotation of the fourth elliptical gear 36 also drives the first The elliptical gear 32 rotates.

Referring to FIG. 3A and FIG. 3B together, the first elliptical gear 32, the second elliptical gear 33, the third elliptical gear 35, and the fourth elliptical gear 36 have long sides a1, a2, a3, a4, and a short side bl, respectively. B2, b3, b4. From the basic physical formula, the velocity is equal to the product of the radius and the angular velocity, that is, v = r * co. When the speed is constant, the angular velocity has an inverse relationship with the radius, that is, the larger the radius, the smaller the angular velocity; the smaller the radius, the larger the angular velocity. In other words, when the short side bl of the first elliptical gear 32 meshes with the long side a4 of the fourth elliptical gear 36, although the first elliptical gear 32 and the fourth elliptical gear 36 have the same speed, due to the difference in radius, Therefore, the short side bl of the first elliptical gear 32 obtains a large angular velocity ω ΐ , and the long side a4 of the fourth elliptical gear 36 obtains a small angular velocity ω 4 . Therefore, when the rotation time is the same, the rotation angle of the first oval gear 32 is larger than the rotation angle of the fourth oval gear 36.

At the same time, the rotation of the fourth elliptical gear 36 will drive the rotation of the third elliptical gear 35, and therefore, the third elliptical gear 35 obtains an angular velocity ω3 equal to that of the fourth elliptical gear 36. When the short side b3 of the third elliptical gear 35 meshes with the long side a2 of the second elliptical gear 33, although the third elliptical gear 35 and the second elliptical gear 33 have the same speed, due to the difference in radius, The short side b3 of the three elliptical gear 35 obtains a large angular velocity ω3, and the long side a2 of the second elliptical gear 33 obtains a small angular velocity ω2. Therefore, when the rotation time is the same, the rotation angle of the third elliptical gear 35 is larger than the rotation angle of the second oval gear 33. As can be seen from the above, the angle of rotation of the first elliptical gear 32 is greater than the angle of rotation of the second elliptical gear 33.

Therefore, the meshing relationship and the rotation angle of the first elliptical gear 32, the second elliptical gear 33, the third elliptical gear 35, and the fourth elliptical gear 36 can be derived from the above formula, and will not be described below.

Further, regarding the case where the pistons operate in the annular cylinder block 234, the spatial variation relationship between the change of the angular velocity and the inhalation portion, the compression portion, the explosion portion, and the exhaust portion is described with reference to the following drawings, and the first reference is made according to the drawings. The angular relationship of the elliptical gear 32, the second elliptical gear 33, the third elliptical gear 35, and the fourth elliptical gear 36 under different angular velocities.

Please refer to FIG. 4A, which is a front view of the rotary engine 2 of the present invention; and FIG. 4A is a perspective view of the rotary engine 2 of the present invention. As shown in FIG. 4A and FIG. 4B, when the second piston 252 starts to be rotated by the thrust generated by the explosion portion toward the fifth piston 255, since the second piston 252 and the first piston 251 are fixed to the outer drive shaft 24, Therefore, the first piston 251 is rotated toward the sixth piston 256, and an intake portion is formed between the first piston 251 and the third piston 253. As can be seen from FIG. 4, the second elliptical gear 33 engages the shorter side of the third elliptical gear 35 with the longer side. According to the above physical formula, the angular velocity (or the angle of rotation) of the second elliptical gear 33 is smaller than that of the third elliptical gear 35. The angular velocity (or angle of rotation). The angular velocity of the fourth elliptical gear 36 and the third elliptical gear 35 are the same, and the longer side is engaged with the shorter side of the first elliptical gear 32. The angular velocity (or the angle of rotation) of the fourth elliptical gear 36 is smaller than that. The angular velocity (or angle of rotation) of the first elliptical gear 32. In other words, the angular velocity (or the angle of rotation) of the second elliptical gear 33 is smaller than the angular velocity (or the angle of rotation) of the first elliptical gear 32; the angular velocity (or the angle of rotation) of the first elliptical gear 32 is greater than that of the second elliptical gear The angular velocity (or the angle of rotation) of 33, so that when the first piston 251 is rotated toward the sixth piston 256 and the second piston 252 is rotated toward the fifth piston 255, the first piston 251 and the second piston 252 The angular velocity (or the angle of rotation) is greater than the angular velocity (or angle of rotation) of the fifth piston 255 and the sixth piston 256 (the third piston 253 and the fourth piston 254 are still still with the fifth piston 255 and the sixth) The piston 256 is actuated simultaneously). 4A and 4B, the fourth elliptical gear 36 is rotated to 45 degrees. At this time, the initial space of the suction portion is about 5 degrees (this angle is an example, and is not limited to the angle, the same applies hereinafter), and The first piston 251 is rotated at a relatively fast angular velocity to gradually increase the space of the suction portion formed with the third piston 253, forming the situation of FIG. 5, wherein the fourth elliptical gear 36 is rotated to 90 degrees, at this time, the suction portion The space is approximately 55 degrees in size and continues to operate as shown in Figure 6. In Fig. 6, the fourth elliptical gear 36 is rotated to 135 degrees, and at this time, the space of the suction portion is about 105 degrees, which is the case where the suction portion space is the largest in this embodiment.

Referring to FIG. 6, when the sixth piston 256 and the fourth piston 254 start to be rotated by the thrust generated by the explosion portion and rotate toward the second piston 252, the third piston 253 also starts to rotate toward the first piston 251, and the third piston is caused. A compression portion is formed between the first pistons 251. As can be seen from Fig. 6, the first elliptical gear 32 engages the shorter side of the fourth elliptical gear 36 with the longer side. According to the above physical formula, the angular velocity of the first elliptical gear 32 is smaller than the angular velocity of the fourth elliptical gear 36. The angular velocity of the third elliptical gear 35 and the fourth elliptical gear 36 are the same, and the longer side is engaged with the shorter side of the second elliptical gear 33. The angular velocity of the third elliptical gear 35 is smaller than that of the second elliptical gear 33. Angular velocity. In other words, the angular velocity of the first elliptical gear 32 is smaller than the angular velocity of the second elliptical gear 33, so that when the third piston 253 and the fifth piston 255 are rotated toward the first piston 251, while the fourth piston 254 and the sixth piston 256 are facing When the two pistons 252 are rotated, the angular velocity (or the angle of rotation) of the first piston 251 and the second piston 252 is smaller than the angular velocities of the third piston 253, the fifth piston 255, and the fourth piston 254 and the sixth piston 256. In FIG. 6, the fourth elliptical gear 36 is rotated by 135 degrees. At this time, the initial space of the compression portion is about 105 degrees. When the third piston 253 and the fifth piston 255 are rotated at a faster angular velocity, the first and second pistons 255 are gradually reduced and first. The compression portion space formed by the piston 251, up to the position of Fig. 7, has a final space size of about 5 degrees.

Next, as shown in FIG. 7, when the first piston 251 starts to be rotated by the thrust generated by the explosion portion toward the sixth piston 256, an explosion portion is formed between the first piston 251 and the third piston 253. As can be seen from Fig. 7, the second elliptical gear 33 engages the shorter side of the third elliptical gear 35 with the longer side. According to the above physical formula, the angular velocity of the second elliptical gear 33 is smaller than the angular velocity of the third elliptical gear 35. The angular velocity of the fourth elliptical gear 36 and the third elliptical gear 35 are the same, and the longer side is engaged with the shorter side of the first elliptical gear 32. The angular velocity of the fourth elliptical gear 36 is smaller than that of the first elliptical gear 32. Angular velocity. In other words, the angular velocity of the second elliptical gear 33 is smaller than the angular velocity of the first elliptical gear 32, so that when the first piston 251 is rotated toward the sixth piston 256 and the second piston 252 is rotated toward the fifth piston 255, the first piston 251 is The angular velocity of the second piston 252 is relative to the third piston 253, the fifth piston 255, and the fourth piston 254, the sixth piston 256. The angular velocity is too big. In FIG. 7, the fourth elliptical gear 36 is rotated to 225 degrees. At this time, the initial space of the explosion portion is about 5 degrees, and the first piston 251 is rotated at a faster angular velocity to gradually increase with the third piston 253. The blast space, up to the position of Figure 8.

Referring to FIG. 8 again, when the fifth piston 255 and the third piston 253 start to be rotated by the thrust generated by the explosion portion toward the first piston 251, between the fifth piston 255, the third piston 253 and the first piston 251 An exhaust portion is formed. As can be seen from Fig. 8, the first elliptical gear 32 engages the shorter side of the fourth elliptical gear 36 with the longer side. According to the above physical formula, the angular velocity of the first elliptical gear 32 is smaller than the angular velocity of the fourth elliptical gear 36. The angular velocity of the third elliptical gear 35 and the fourth elliptical gear 36 are the same, and the longer side is engaged with the shorter side of the second elliptical gear 33. The angular velocity of the third elliptical gear 35 is smaller than that of the second elliptical gear 33. Angular velocity. In other words, the angular velocity of the first elliptical gear 32 is smaller than the angular velocity of the second elliptical gear 33, so that when the fifth piston 255, the third piston 253 are rotated toward the first piston 251, and the fourth piston 254, the sixth piston 256 are facing the second When the piston 252 is rotated, the angular velocities of the first piston 251 and the second piston 252 are smaller than the angular velocities of the fifth piston 255, the third piston 253, the fourth piston 254, and the sixth piston 256. In FIG. 8, the fourth elliptical gear 36 is rotated to 315 degrees. At this time, the initial space of the exhaust portion is about 105 degrees, and the third piston 253 and the fifth piston 255 are rotated at a relatively fast angular velocity to be gradually reduced. The exhaust portion space formed by the first piston 251 is returned to the position of FIGS. 4A and 4B.

In the above drawings, the inner drive shaft 28 or the intermediate drive shaft 26 rotates counterclockwise, but if the intake port and the exhaust port are exchanged, the clockwise direction is rotated. Moreover, the description of the position is also convenient for indicating the position where the piston is in the stroke of the intake portion, the intake portion, the explosion portion or the exhaust portion, and the relative positional relationship between the piston and the elliptical gear, and the scope of the present invention is also Not limited to this.

In addition, the description of the cooling system of this rotating engine is as follows:

Regarding the cooling portion of the inner annular cylinder block 22, as shown in Fig. 2A, when the inner annular cylinder block 22 is engaged with the gear case 21, a closed space is formed. The inner annular cylinder block 22 is provided with two cooling liquid flow ports 224, and the inner annular cylinder block 22 is cooled when the cooling liquid flows through the two cooling liquid flow ports 224.

Regarding the cooling portion of the outer annular cylinder block 23, as shown in Fig. 2A, when the outer annular cylinder block 23 is engaged with the outer annular cylinder cover plate 29, a closed space is formed. The outer annular cylinder block 23 is provided with two cooling liquid flow ports 236 through which the outer annular cylinder block 23 is cooled when the cooling liquid flows through the two cooling liquid flow ports 236.

Regarding the cooling portion of the first piston 251, as shown in FIG. 2A and FIG. 2B, the first piston 251 is provided with a cooling liquid flow port 2514 and a cooling liquid flow port 2515. The two cooling liquid flow ports 2514, 2515 are connected first. A confined space within the piston 251. The outer drive shaft 24 is provided with at least one cooling liquid flow port 245 and at least one cooling liquid flow port 246. The inner annular cylinder block 22 is on the surface of the annular cylinder block 234, in the cold At the liquid flow port 245 and the cooling liquid flow port 246, a cooling liquid flow path 227 and a cooling liquid flow path 228 are provided. Further, the inner annular cylinder block 22, which is perpendicular to the passage, is provided with two cooling liquid flow ports 225. ο. After the first piston 251 engages the outer drive shaft 24, and the outer drive shaft 24 engages the inner annular cylinder block 22, the cooling liquid can be made. The cooling liquid circulation port and the cooling liquid flow path are circulated to achieve the purpose of cooling the first piston 251. The same applies to the second piston 252.

Regarding the cooling portions of the third piston 253 and the fifth piston 255, as shown in FIG. 2A, the third piston 253 is provided with two cooling liquid flow pipes (not shown in the drawing, and the form and the cooling of the liquid flow of the fourth piston 254 are circulated. The tube 2545 is the same), the tube body is formed in an arc shape, and the center of the arc is the same as the axis of each of the transmission shafts of the plane in which the arc is located, and the two cooling liquid flow tubes communicate with a sealed space in the third piston 253. The fifth piston 255 is provided with two cooling liquid flow tubes 2555, the tube body is formed in an arc shape, the center of the arc is the same as the axis of each of the transmission shafts in the plane of the arc, and the inner tube diameter is just the same as the cooling liquid flow tube. The outer diameter of the 2536 is compatible. Here (not shown in the figure, the shape is the same as that of the cooling liquid flow tube 2545). The two cooling liquid flow tubes are provided with more than one type 0 rubber ring on the outer edge of the tube near the upper vertical arc center tangential plane of the opening (Fig. Show) to seal the cooling liquid inside these tubes and avoid flowing outside the piston. The bottom of the convex birch portion 2551 of the fifth piston 255 is provided with two cooling liquid flow ports 2554, and communicates with the cooling liquid flow pipe 2536, respectively. The two groove portions 284 of the inner drive shaft 28 are also respectively provided with two cooling liquid flow ports 285 which are respectively connected to the cooling liquid flow port 281 and a cooling liquid flow port 287. When the convex birch portion 2551 of the fifth piston 255 is engaged with the groove portion 284 of the inner transmission shaft 28, the cooling liquid flow port 2554 and the cooling liquid flow port 285 of the two groove portions 284 of the inner transmission shaft 28 can communicate with each other. Therefore, when the above members are joined, the cooling liquid can be circulated to the cooling liquid flow ports for the purpose of cooling the third piston 253 and the fifth piston 255. The same applies to the fourth piston 254 and the sixth piston 256.

The manner in which the airtightness of the rotating engine of the present invention is maintained is as follows:

The first piston 251 is provided with three piston ring groove portions 2513, and three first piston ring grooves 2516 are respectively inserted into the three piston ring groove portions 2513, and the first piston 251 can be ensured by the action of the piston ring. The air tightness. The same applies to the second piston 252.

The third piston 253 is provided with a piston ring groove portion 2532, and is inserted into the piston ring groove portion 2532 by a second type piston ring 2534. Under the action of the piston ring, the airtightness of the third piston 253 during operation can be ensured. . The same is true for the fourth piston 254.

The fifth piston 255 is provided with a piston ring groove portion 2552, and is inserted into the piston ring groove portion 2552 by a first type piston ring 2516. Under the action of the piston ring, the airtightness of the fifth piston 255 during operation can be ensured. . The sixth piston 256 is also the same.

As can be seen from the above, by the rotary engine of the present embodiment, the activities provided in the annular cylinder block 234 are made The plug uses the rotation method to complete the cycle of the reciprocating power of the traditional engine, which makes the rotating engine operate smoothly and reduces the loss of kinetic energy. In addition, the rotating engine fully utilizes the space in the annular cylinder block 234 to complete the cycle of the power, and achieves the cooling and airtight effect of the rotating engine, thereby improving the disadvantage that the conventional engine cannot effectively utilize the internal space of the cylinder at present. Make it a much smaller size.

In addition, regarding the change of the compression ratio of the rotating engine, the calculation method of the compression ratio of the rotating engine is to complete the "intake"; the set of pistons to be "compressed", the original space in the annular cylinder block 234, except The ratio of the space in which the set of pistons completes compression. To change the "compression ratio", change the "the final compression space of the piston".

In the above embodiment, since the first elliptical gear 32, the second elliptical gear 33, the third elliptical gear 35, and the fourth elliptical gear 36 mesh with each other at a fixed angle, and the compression ratio increase/decrease control mechanism 3 is not yet operated. Next, each piston performs a stroke of inhalation, compression, explosion, and exhaust in a fixed space (angle) within the annular cylinder block 234. However, with the compression ratio increase/decrease control mechanism 3 of the present invention, the "piston completes the compression space" can be changed, and the compression ratio of the present rotary engine can be changed.

The compression ratio increase/decrease pusher 38, the compression ratio increase/decrease gear mount 39, the half-type bearing 30, the compression ratio increase/decrease gear mount cover 31, the third piston 253, the fourth piston 254, and the fifth The piston 255, the sixth piston 256, the intermediate transmission shaft 26, the inner transmission shaft 28, and the second elliptical gear 33 may constitute a compression ratio increase/decrease control mechanism 3.

The compression ratio increase/decrease gear holder 39 is provided with a rotation accommodation space 391, two screw holes 392, and two slide shaft holes 393. The compression ratio increase/decrease gear mount cover plate 31 is provided with two screw holes 312 and two slide shaft holes 313. The compression ratio increase/decrease gear mount cover 31 can be covered by the compression ratio increase/decrease gear mount 39. The two sliding shaft holes 393 and the two sliding shaft holes 393 are respectively axially disposed on the two sliding shafts 216 of the gear housing 21.

The second elliptical gear 33 has an annular flange portion 333. The two half-shaped bearings 30 cover the annular flange portion 333 and merge into an annular bearing. The annular bearing is disposed in the rotation accommodating space 391 of the compression ratio increase/decrease gear holder 39, increases or decreases the coverage of the gear mount cover 31 via the compression ratio, and increases and decreases the compression ratio gear mount 39 and After the cover shaft is disposed on the sliding shaft 216, the compression ratio increase/decrease gear mount 39, the compression ratio increase/decrease gear mount cover 31 and the second elliptical gear 33 can be front and rear on the slide shaft 216. slide. In addition, the two compression ratio increase/decrease pushers 38 are fixed on the gear box body 21, and a push shaft 381 is respectively bored through a hole 217, and the compression ratio increase/decrease gear mount 39 and the compression ratio increase and decrease respectively. Two screw holes 312 and two screw holes 392 of the gear mount cover 31 are fixed to each other. Therefore, the compression ratio increase/decrease pusher 38 can be used to push the mutually engaged second elliptical gears 33 to slide forward and backward on the slide shaft 216. As previously described, the inner drive shaft 28 has a diagonal pin groove portion 282 disposed on the shaft body 283 in the gear housing 21. The middle drive shaft 26 has a diagonal pin groove portion 262 which is also disposed on the hollow shaft body 263 in the gear case body 21. The shaft body 283 of the inner transmission shaft 28 is disposed through the shaft hole 261, and the oblique bolt groove portion 282 protrudes from the oblique bolt groove portion 262. Both the oblique pin groove portion 282 and the oblique pin groove portion 262 are grooved in the axial center, and are inclined at a certain angle equal to each other.

Further, the second elliptical gear 33 has an oblique hub groove portion 331 that fits the oblique pin groove portion 282 and an oblique hub groove portion (not shown) that has a matching oblique pin groove portion 262. The oblique hub groove portion 331 is grooved to the oblique pin groove portion 282, and the oblique hub groove portion (not shown) is grooved to the oblique pin groove portion 262. When the second elliptical gear 33 slides on the sliding shaft 216, the intermediate transmission shaft 26 and the inner transmission shaft 28 are rotated clockwise at the same angle and at the same angle based on the relationship of the inclined hub groove portion to the oblique bolt groove portion. The counterclockwise rotation, and the angle of rotation will vary depending on the distance the second elliptical gear 33 slides on the sliding shaft 216.

As mentioned before, the first piston 251, the second piston 252, the third piston 253, the fourth piston 254, the fifth piston 255, and the sixth piston 256 are alternately disposed within the annular cylinder block 234. The first piston 251 and the second piston 252 are respectively provided with a half-type combustion chamber 2512 on the front and rear piston faces perpendicular to the sliding direction of the piston, and the remaining pistons only face the first piston 251 and the second piston 252 half-type combustion chamber 2512. A semi-combustion chamber 2512 is provided on the piston face. In other words, the present invention, by the combination described above, causes the two piston faces having the semi-type combustion chamber 2512 to form a working space for suction, pressure, explosion, and discharge, and simultaneously forms four working spaces. However, for the piston face without the semi-type combustion chamber 2512, an adjustment portion is formed to adjust the compression ratio of the rotary engine of the present invention when the compression ratio increase/decrease control mechanism 3 operates, and the space is not provided for suction, Pressure, explosion, and row function.

Because the third piston 253 and the fourth piston 254 are connected to the middle transmission shaft 26, the fifth piston 255 and the sixth piston 256 are connected to the inner transmission shaft 28, and the inner transmission shaft 28 is axially disposed on the middle transmission shaft 26, so When the second elliptical gear 33 slides on the sliding shaft 216, the third piston 253 and the fourth piston 254 which are connected to the middle transmission shaft 26 and the fifth piston 255 and the sixth piston which are connected to the inner transmission shaft 28 are arranged. 256 are clockwise rotation of a certain angle and counterclockwise rotation of the same angle. When the design angle is appropriate, one piston which combines the third piston 253 and the fifth piston 255 and the other piston which is composed of the fourth piston 254 and the sixth piston 256 are caused to expand or become smaller. Then, when the expansion of the piston is increased and the compression stroke is completed at the same time, the expansion of the piston becomes large, and the space after compression becomes small, so that the compression ratio of the rotary engine becomes large. In the same manner, the piston becomes closed and becomes smaller, and the space after compression becomes larger, so that the compression ratio of the present rotary engine becomes smaller.

As shown in FIG. 4B, a perspective view of the rotary engine, when the plane of the second elliptical gear 33 near the outer side perpendicular to the rotation axis is flush with the plane perpendicular to the rotation axis of the third elliptical gear 35, the first activity The angle between the plug 251 and the third piston 253 is about 5 degrees. As shown in Fig. 9, when the compression ratio increase/decrease pusher 38 pushes the compression ratio increase/decrease gear mount 39, the second oval gear 33 is simultaneously urged to translate in the rotational axis. The tooth width of the third elliptical gear 35 is twice that of the second elliptical gear 33. When the plane of the second elliptical gear 33 near the inner side perpendicular to the rotation axis is flush with the plane perpendicular to the rotation axis of the inner side of the third elliptical gear 35, the third piston is operated based on the above-described compression ratio increase/decrease control mechanism 3 253 and the fifth piston 255 produce the effect of "expansion and enlargement", causing the angle between the first piston 251 and the third piston 253 to be only about 1.5 degrees. It is particularly emphasized that the change from about 5 degrees to about 1.5 degrees can be continuously changed, not only variable by about 5 degrees and about 1.5 degrees, and is also described together.

In summary, the rotary engine 2 can change the compression ratio of the rotary engine 2 by the operation of the compression ratio increase/decrease control mechanism 3.

In addition, when the third piston 253 and the fifth piston 255 of the rotary engine 2 of the present invention are redesigned to merge them into one piston, the fourth piston 254 and the sixth piston 256 are also combined into one piston, and the middle transmission shaft is also 26 and the inner drive shaft 28 are redesigned and combined into one drive shaft, wherein the middle drive shaft 26 and the inner drive shaft 28 can be integrally formed to form a drive shaft, and the rest can be realized except for the compression ratio increase/decrease control mechanism 3. The above-described rotation engine performs the functions of suction, pressure, explosion, and discharge in a rotating manner, and is also described together.

The foregoing is illustrative only and not limiting. Equivalent modifications or variations of the present invention are intended to be included within the scope of the appended claims.

Claims

claims

1. A rotary engine, including:

an inner drive shaft;

One drive shaft;

An outer transmission shaft, the inner transmission shaft, the middle transmission shaft and the outer transmission shaft are nested with each other;

Three pairs of pistons, the inner drive shaft, the middle drive shaft and the outer drive shaft are respectively fixed to the corresponding pair of pistons, and each pair of pistons is staggered and symmetrically arranged;

A first elliptical gear, which is fixedly connected to the outer transmission shaft;

A second elliptical gear, the inner transmission shaft and the middle transmission shaft respectively have an oblique spline groove with different angles, and are connected to the second oval gear with these oblique spline grooves;

A third elliptical gear and a fourth elliptical gear intersect perpendicularly and are fixed to a power output shaft. The first elliptical gear meshes with the fourth elliptical gear. The second elliptical gear meshes with the third elliptical gear.

2. The rotary engine as claimed in claim 1, further comprising:

a gear box with an accommodation space; and

An annular cylinder block is provided outside the accommodation space of the gear box, and includes a first shaft hole, a second shaft hole and an accommodation space, wherein the inner transmission shaft has two shaft bodies, one of which is The shaft body is installed in the first shaft hole of the annular cylinder body, and the other shaft body is installed in the second shaft hole. The middle transmission shaft has an shaft hole and a hollow shaft body. The inner transmission shaft is installed in the first shaft hole. The shaft body in the second shaft hole is passed through the shaft hole of the middle transmission shaft. The outer transmission shaft has an shaft hole and a hollow shaft body. The hollow shaft body of the middle transmission shaft is partially passed through the shaft hole. The shaft hole of the outer transmission shaft, the shaft body of the inner transmission shaft partially penetrates the hollow shaft body, and penetrates the second shaft hole of the annular cylinder body and partially protrudes outside the annular cylinder body, and the three The pair of pistons includes a first piston, a second piston, a third piston, a fourth piston, a fifth piston and a sixth piston. The first piston and the second piston are arranged on the annular cylinder body. The third piston and the fourth piston are arranged in the accommodation space of the annular cylinder body and fixed to the outer transmission shaft. The fifth piston and the third piston are fixed to the middle transmission shaft. The six pistons are disposed in the accommodating space of the annular cylinder body and are fixed to the inner transmission shaft. The first elliptical gear has a gear part. The first elliptical gear is disposed in the accommodating space of the gear box. , and is connected with the shaft body of the outer transmission shaft partially protruding from the annular cylinder body, the second elliptical gear has a gear part, the second elliptical gear is arranged in the accommodation space of the gear box, and Connected to the middle transmission shaft and the shaft body of the inner transmission shaft that partially protrudes from the annular cylinder block, the third elliptical gear is disposed in the accommodation space of the gear box, and has a gear part, the gear part of the third elliptical gear meshes with the gear part of the second elliptical gear, the fourth elliptical gear is disposed in the accommodation space of the gear box, and has a gear part, the third elliptical gear The gear portion of the four-elliptical gear meshes with the gear portion of the first elliptical gear, and the power output shaft is pivoted on the gear box.

3. The rotary engine as claimed in claim 2, wherein the annular cylinder block is an annular hollow cylinder composed of two semicircular annular cylinder blocks, and the annular cylinder block is provided with an air inlet, an exhaust port and more than one Ignition port.

4. The rotary engine as claimed in claim 3, wherein the annular cylinder block is provided with more than one fuel injection inlet.

5. The rotary engine as claimed in claim 4, wherein each piston is arranged sequentially in the annular cylinder body, with a space between each piston, and these spaces respectively form a suction part, a compression part, and an explosion part. , one exhaust part and two regulating parts.

6. The rotary engine of claim 5, wherein the first piston, the second piston, the third piston, the fourth piston, the fifth piston and the sixth piston respectively have two piston surfaces, Each piston surface of the first piston and the second piston is provided with a half-type combustion chamber. The third piston, the fourth piston, the fifth piston and the sixth piston only face the first piston and the second piston. The piston surface is equipped with a half-type combustion chamber.

7. The rotary engine as claimed in claim 6, wherein the air inlet and the two piston surfaces adjacent to which are provided with half-type combustion chambers form the suction portion, and the exhaust port and adjacent to which are provided with half-type combustion chambers form the suction portion. The two piston surfaces of the chamber form the exhaust part, the pilot port and the two piston surfaces adjacent to the half-type combustion chamber form the explosion part, and the space between the two pistons is formed between the air inlet and the pilot port. The compression part and the piston surfaces of the two pistons facing the air inlet have a half-type combustion chamber. The adjustment part is formed by the space between the two pistons. The piston surfaces facing the adjustment part are not provided with a half-type combustion chamber. .

8. The rotary engine as claimed in claim 7, wherein a hollow plug is provided on a piston surface facing the adjusting part, the hollow plug is arc-shaped, and the center of the arc is the same as the axis center of each transmission shaft in the plane where the arc is located. , the hollow plug has a plug surface, the plug surface has a hole for flowing liquid, and the other piston surface A plug cylinder is provided. The plug cylinder is arc-shaped, and the center of the arc is the same as the axis center of each transmission shaft in the plane where the arc is located. It is used to accommodate the hollow plug. The interior of the plug cylinder can accommodate circulating liquid.

9. The rotary engine as claimed in claim 8, wherein a piston surface facing the adjustment part is provided with at least one first cooling liquid circulation tube, the first cooling liquid circulation tube is arc-shaped, and the center of the arc is the same as the arc. The first cooling liquid flow tube is connected to a closed space in the piston at the axis center of each transmission shaft in the plane. The other piston surface is provided with at least a second cooling liquid flow pipe. The second cooling liquid flow pipe is arc-shaped. The center of the circle is the same as the axis center of each drive shaft in the plane where the arc is located, and the inner diameter of the second cooling liquid flow tube matches the outer diameter of the first cooling liquid flow pipe. These pistons connect the inner drive shaft, the The bottoms of the middle transmission shaft and the outer transmission shaft are each provided with at least one cooling liquid flow port, and are respectively connected with the first cooling liquid flow pipe and the second cooling liquid flow pipe. The inner transmission shaft is connected to these corresponding pistons. At least one cooling liquid flow port is respectively provided, which is respectively connected with another cooling liquid flow port that passes through the axis center of the inner transmission shaft. When the fifth piston is engaged with the inner transmission shaft, the aforementioned cooling liquid flow holes are connected to each other. Connected.

10. The rotary engine as claimed in claim 1, wherein the second elliptical gear connected with the inclined bolt groove of the inner drive shaft and the middle drive shaft is pushed to move at the center of the rotation axis, so that the second elliptical gear is connected The inner transmission shaft and the middle transmission shaft rotate at different angles, causing the corresponding pistons fixed on the inner transmission shaft and the middle transmission shaft to expand or close to become smaller.