JPH03202637A - Rotary type internal combustion engine - Google Patents

Abstract

PURPOSE:To obtain a high output from a rotary type internal combustion engine by fitting a plurality of rotors slidably in a ring-shaped cylinder chamber, thereby forming a plurality of working chambers in the cylinder chamber, and inducing in each working chamber the suction, compression, combustion, and exhaust of four strokes within a turn of the output shaft one after another with a certain phase difference. CONSTITUTION:A ring-shaped cylinder part 14 is formed concentrically around a body part 12 assuming a hollow cylinder, and four identically shaped rotors 22 assuming a curved circular column are slidably fitted in the circular profile ring-shaped cylinder chamber 20 of this cylinder part 14, and thereby working chambers 23 are partitioned between adjoining rotors 22, 22. The rotors 22, 22 facing each other with an output shaft 16 interposed are coupled together by approx. cylindrically shaped coupling parts 24, 26, which are, through connecting rods 54, 54, connected with a pair of crank shafts 40, 41 held rotatably on the major dia. part 18 of the output shaft 16 in two places oppositely situated in the diametric direction. A suction hole 64 is formed in the capacity expanding region of the cylinder part 14, while an exhaust hole 68 is provided the capacity shrinking region situated downstream the mentioned suction hole 64 about the rotor rotating direction.

Description

Detailed Description of the Invention (Technical Field) The present invention has a structure that is lighter and more compact than a reciprocating engine and can provide greater output, and has better airtightness than the Wankel-type reciprocating engine currently in practical use. The present invention relates to a rotary internal combustion engine that can provide good retention and wear resistance.

(Background Art) Among internal combustion engines such as automobile engines, the most popular one today is a reciprocating piston type reciprocating engine. However, this reciprocating engine has a small output compared to the exhaust II (cylinder volume) (and generally requires intake and exhaust valves and a cam mechanism to drive them, so the overall engine configuration is complicated. As the size increases, there is a problem that the weight increases.

On the other hand, the Wankel rotary engine, which rotates a triangular rotor inside a cocoon-shaped casing, has also been put into practical use. In such a Wankel rotary engine, there are three explosion strokes per revolution of the rotor, so it is possible to obtain a larger output than a reciprocating engine compared to a reciprocating engine. Since a cam mechanism or the like is not required, it has the advantage that the entire engine can be made lighter and more compact than a reciprocating engine.

However, due to the unique shape of the rotor, such a Wankel-type rotary engine has the problem that it is difficult to maintain airtightness between the working chambers separated by the rotor, and the top part of the triangular rotor is Since the rotor is in line contact with the inner surface of the rotor, there are problems in that the wear resistance of the rotor is poor and durability is poor.

(Problem to be solved) The present invention was made against the background of the above-mentioned circumstances, and its object is to be able to obtain a large output with a structure that is lighter and more compact than conventional reciprocating engines. Moreover, it is an object of the present invention to provide a rotary internal combustion engine that can improve airtightness and durability compared to Wankel rotary engines.

(Solution Means) In order to solve this problem, the rotary internal combustion engine according to the present invention has a plurality of rotors slidably fitted in an annular cylinder chamber to form a plurality of working chambers in the cylinder chamber. , so that as the rotors rotate, the volumes of adjacent working chambers in the circumferential direction increase and decrease periodically in opposite directions, and the volumes of each working chamber are sequentially adjusted at preset positions in the circumferential direction of the cylinder chamber. The positions of increase and decrease in the volume of the working chambers are such that the rotors are interconnected so as to increase and decrease, and as the rotors rotate, intake, compression, explosion, and exhaust operations are sequentially caused in the working chambers. In connection with this, an intake port, an ignition means, and an exhaust port are provided on the peripheral wall of the cylinder chamber, and the rotor is rotated in the circumferential direction of the cylinder chamber by the explosive action caused by the ignition of the ignition means synchronized with the rotation of the rotor. Furthermore, each rotor is connected to an output shaft disposed at the center of the cylinder chamber, and the rotation of the rotors is taken out by the output shaft.

(Function/Effect) In a rotary internal combustion engine with such a structure, during one revolution of the output shaft, four cycles of intake, compression, explosion, and exhaust are sequentially performed in each working chamber with a constant phase difference. can be caused to occur. For example, if the working chamber is 4
By forming the chamber, it is possible to obtain four explosive strokes per revolution of the output shaft. Therefore, it is possible to increase the output per unit displacement as well as the conventional Wankel rotary engine, and even more so, as with the conventional Wankel rotary engine. Since there is no need for a cam mechanism or the like to drive the engine, the entire engine can be made lighter and more compact than a reciprocating engine, similar to the Wankel rotary engine.

Moreover, since surface contact can be made between the cylinder chamber wall and each rotor, it is possible to ensure better airtightness in each working chamber than in the conventional Wankel-type rotor engine, and there is no sliding contact with the cylinder chamber. This makes it possible to better avoid wear of the rotor caused by the rotor, thereby further improving the durability of the rotor and, ultimately, the lifespan of the internal combustion engine.

(Example) Hereinafter, an example of the present invention will be described in detail based on the drawings.

First, FIGS. 1 and 2 schematically show cross-sectional views showing one embodiment of the present invention. In those figures,
Reference numeral 10 denotes a casing, which is composed of a hollow cylindrical main body 12 and an annular cylinder part 4 formed concentrically around the main body 12. An output shaft 16 is rotatably disposed concentrically through the main body part 12, and the output shaft 16 is provided with a main body part 2.
A large diameter section is formed in the center of the tube.

On the other hand, the cylinder portion 14 is formed with an annular cylinder chamber 20 having a circular cross section, and four rotors 22 having the same shape are arranged to be slidably fitted into the cylinder chamber 20. 21 is a water jacket.

The rotor 22 has a curved cylindrical shape, and piston rings 25 are disposed at both ends of the rotor 22 to maintain airtightness of the working chamber 23 formed between the rotors 22, 22. (omitted in Figure 1). The connecting portions 24 of the rotor 22 facing each other across the output shaft 16 have a phase difference of 180°.
．． They are fixedly connected at 26. As shown in FIGS. 3 and 4, these connecting portions 24 and 26 have a substantially cylindrical shape, and the output shaft is rotatably connected to the cylindrical portions 28 and 30, respectively. 16 large diameter portions 18 from mutually opposite sides in the axial direction. Each corresponding pair of rotors 22, 22 has their cylindrical portions 28.3 on their respective inner circumferential surfaces.
An outward flange portion 32 protruding from the butting end of 0
, 34, and is brought into sliding contact via the piston ring 25 with the distal end surfaces of the outward flange portions 32, 34 on the non-coupling side.

As is clear from FIG. 1, a notch 36 of a constant width is formed in an annular shape in the circumferential direction on the inner circumferential wall of the cylinder portion 14, and the outward flange portion of each connecting portion 24, 26. 32.34 is the notch 3 in the inner circumferential wall of the cylinder portion 14.
6 to each corresponding rotor 22,22. and the outward flange portion 3 of each connecting portion 24,26.
2.34, and between the outward flange portions 32.34 and the wall surface of the notch 36 of the cylinder portion 14.
8 is disposed, and the cylinder chamber 20, that is, the working chamber 23 is kept airtight from the outside.

Further, as is clear from FIG. 2, the piston ring 25 has an annular shape in which the outward flange portion 32.34 of the connecting portion 24.26 is cut out.

Incidentally, a pair of crankshafts 40 and 41 are rotatably held in the large diameter portion 18 of the output shaft 16 at symmetrical positions with respect to the axis. The crankshafts 40, 41 are each 180° in phase with respect to each other.
It has a pair of different crank parts 42, 44, and a central journal 4 that connects the crank parts 42, 44.
6, they are rotatably held on the large diameter portion 18 of the output shaft 16 with the same phase relationship. Also,
Each crankshaft 40,41 has journals 4 at both ends.
At 8.48, they are rotatably held by holding pars 50, 50 extending from the output shaft 16, respectively.

Further, these crankshafts 40.41 connect the connecting portions 24 which are 180° out of phase through connecting rods 54.54 at the crank pins 52, 52 of the crank portions 42.42 on the side facing the connecting portion 24, respectively. pin 5
6.56, and at the crank pins 52, 52 of the crank part 44.44 on the side opposite to the connecting part 26, 18
It is connected to the connecting pins 56, 56 of the connecting part 26 that are out of phase by 0°.

And here, with this, the crankshaft 40
．． 41, the coupling parts 24 and 26 and, in turn, the rotor 22, 22 connected by the coupling part 24 and the coupling part 2.
The rotors 22 and 22 connected at 6 are periodically moved relative to each other with a constant stroke in the circumferential direction, so that the volumes of the working chambers 23 adjacent to each other in the circumferential direction are periodically increased and decreased in mutually opposite directions. It has become.

On the other hand, planetary gears 60.60 of the same shape are fixed to the journals 48.48 at both ends of each crankshaft 40.41, and the planetary gears 60.60 of the same shape are fixed to the casing 12 in a state of meshing with the planetary gears 60.60, respectively. , a gear 62°62 with a gear ratio twice that is fixedly installed. and,
Here, this means that for one revolution of the rotor 22, that is, one revolution of the output shaft 16, the crankshaft 4
041 rotates twice, and the volume of each working chamber 23 is periodically increased or decreased twice per revolution at the same position in the circumferential direction of the cylinder chamber 20, with the same volume variation pattern.

Here, as shown in FIG.
, an intake port 64 is provided corresponding to a first volume expansion region where the volume of each working chamber 23 increases as the rotor 22 rotates.
is formed, and a spark plug 6 as an ignition means is formed corresponding to a first volume contraction limiting region following this first volume expansion region.
6 is provided. Then, an exhaust port 68 is provided corresponding to a second volume contraction area portion downstream of the first volume contraction limit portion in the rotor rotational direction, and a spark plug synchronized with the rotation of the rotor 22 is provided in each working chamber 23. By the ignition action of 66, each operation of intake, compression, explosion, and exhaust can be successively triggered with a certain phase difference from each other.

That is, the fuel gas taken into the working chamber 23 from the intake port 64 due to the volume expansion action according to the rotation of the rotor 22 is compressed by the volume contraction action of the working chamber 23 in the first volume contraction region, resulting in the first volume contraction. After reaching the limit position and being ignited and exploded by the spark plug 66, the combustion gas is exhausted to the outside from the exhaust port 64 by the volume contraction action of the working chamber 23 in the second volume contraction area. In this way, each operation (stroke) of intake, compression, explosion, and exhaust is sequentially caused in each working chamber 23 with a certain phase difference, so that each rotor 22
is continuously rotated, and as a result, the output shaft 16 is continuously rotated via the crankshaft 40, 41.

In this way, in the internal combustion engine of this embodiment, each working chamber 23 performs four cycles of intake, compression, explosion, and exhaust every time each working chamber 23 rotates once. In other words, four explosion strokes are performed per revolution of the output shaft 16, and therefore, the output per unit displacement can be as large as or even higher than that of the conventional Wankel-type low-crit engine. . and,
In addition, the internal combustion engine of this embodiment can perform such operations without providing intake and exhaust valves or cam mechanisms to drive them, so it is simpler and easier to operate than a reciprocating engine. This allows for a lightweight and compact structure.

Furthermore, as is clear from the above description, the cylinder chamber 20
Since the inner wall of the engine and each rotor 22 are in surface contact, and the sliding contact between them is performed via the piston ring 25, the airtightness of each working chamber 23 is significantly improved compared to the conventional Wankel type rotor engine. This also effectively prevents wear of the rotor 22 and improves its durability.

Furthermore, in this embodiment, the planetary gear 60 and the stove throat 54
Since two sets of power transmission mechanisms, such as In comparison, it has advantages in terms of improving the strength and reducing the weight of the power transmission mechanism, and furthermore, in terms of reducing energy loss due to a reduction in the moment of inertia. Note that it is also possible to provide three or more sets of driving force transmission mechanisms for each of the connecting portions 24 and 26.

In addition, compared to a reciprocating engine, the internal combustion engine of this embodiment has reduced noise, widened optimal output control by changing the opening degree of the intake and exhaust ports, and fuel consumption rate by adopting a low-pressure fuel injection method. It also has the advantage of eliminating the need for a suction/exhaust pulp mechanism, such as improving air flow and making exhaust gas cleaner, and that various effects can be expected due to rotary piston motion.

Next, another embodiment of the present invention will be described based on FIG. Components having the same functions as those in the embodiment described above will be denoted by the same reference numerals, and detailed explanations will be omitted unless necessary.

In this embodiment, the casing 10 has a structure in which a main body part 12 and a cylinder part 14 are integrally connected in the axial direction.
An output shaft 16 is disposed passing through the center. The cylinder chamber 20 is formed around the output shaft 16 so as to be concentric with the shaft 16 and have an arch-like cross-sectional shape.

Here, the rotor 22 has an arch-like cross-sectional shape corresponding to the cross-sectional shape of the outer peripheral part of the cylinder chamber 20, and as in the embodiment described above, the connecting portions of the rotor 22 have a phase difference of 180°. They are fixedly connected to each other at 24 and 26. The connecting portions 24 and 26 are connected to the cylindrical portions 28 and 3, respectively.
The outer flange portions 32.34 extend from one end of the cylindrical portion 28.30, and are rotatably fitted to each other in the cylindrical portion 28.30. The cylindrical portion 28 is rotatably slidably contacted with each other and with the side wall of the cylinder 20.
．． The other end of 30 protrudes into the main body 12 of the casing 10, and is rotatably fitted to the output shaft 16 at the cylindrical portion 28 of the inner coupling portion 24, while the outer coupling portion 26
The cylindrical portion 30 is rotatably fitted into a through hole 72 formed in a partition wall 70 of the casing 10 .

These connecting portions 24.26 are connected to each corresponding rotor 2 at the tip of each outward flange portion 32.34.
2, 22, and the rotor 22 on the non-coupled side at the tip surface of each outward flange portion 32, 34.
, 22 so as to be rotatably fitted. Although not shown in the drawings, each rotor 22 is provided with a piston ring 25 similar to that of the above embodiment, and between each connecting portion 24.26 and the casing 10 or between the reconnecting portion 24.26. A gasket for keeping each working chamber 23 airtight from the outside space is appropriately placed between the two.

Incidentally, a circular ring 74 is fixed to the output shaft 16 in the main body 12 of the casing 1O, and a through hole 7 on the main body 12 side is provided in the partition wall 70 of the casing 1O.
A circular ring 78 is rotatably fitted onto the outer circumferential surface of a cylindrical protrusion 76 forming the open end of the cylindrical ring 76 . A crankshaft 40 is disposed rotatably held in the circular rings 74 and 78 by journals 48 and 48 at both ends. .54 to a connecting pin (both not shown) formed in the cylindrical part 28.30 of the connecting part 24.26. As a result, the volume of the working chamber 23 formed between the rotors 22 and 22 is changed by the rotation of the crankshaft 40, as in the previous embodiment.

Further, a reinforcing rod 80 is disposed in the circumferential circular rings 74, 78 in parallel with the crankshaft 40 and rotatably penetrates the circular rings 74, 78. Planetary gears 60 are rotatably disposed at both ends of the reinforcing iron 80 and the journals 48, 48 at both ends of the crankshaft 40, while the casing 10
Gears 62 are formed at both ends of the main body 12 in the axial direction, and these gears 60, 62 are meshed with each other, and as in the previous embodiment, each time the rotor 22, and therefore the output shaft 16, makes one revolution. , the crankshaft 40 is 2
It can be rotated. In other words, as in the embodiment described above, the volume of each working chamber 23 is increased or decreased twice each time the output shaft 16 rotates once.

And here, the intake port 64. The exhaust port 68 and the spark plug 66 are formed in the same positional relationship as in the previous embodiment with respect to the volume change area of the working chamber 23 in the cylinder chamber 20, so that the output shaft 16 During one rotation of the engine, four cycles of intake, compression, explosion, and exhaust are sequentially caused in each working chamber 23 with a constant phase difference.

Even with an internal combustion engine having such a structure, the same effects as in the embodiment described above can be obtained.

Several embodiments of the present invention have been described in detail above, but these are literal examples. For example, the fitting cross-sectional shape of the cylinder chamber 20 and the rotor 22 may be polygonal, or the rotor 22 may have a mating cross-sectional shape.
The present invention is not limited to these specific examples, such as changing the number of devices arranged, and can be practiced with various changes, modifications, improvements, etc. without departing from the spirit thereof. It goes without saying that.

[Brief explanation of drawings]

FIG. 1 is a front cross-sectional view schematically showing an example of an internal combustion engine according to the present invention, FIG. 2 is a right side cross-sectional view of the same, and FIG. FIG. 4 is a half-cut sectional view showing a rotor component taken out, and FIG.
FIG. FIG. 5 is a front sectional explanatory view schematically showing another embodiment of the present invention. IO: 14: 20: 23: 40°42°60: 64: 68: 80: Casing 12 Cylinder section 16 Cylinder chamber 22 Working chamber 24 41: Crankshaft 44: Crank section 50: Holding bar planetary gear 62: Gear intake Port 66: Spark plug exhaust port 74.78: Circular ring reinforcement Rondo 2 body part: Output shaft: Rotor 26: Connection part Fig. 3 Fig. 4

Claims (1)

[Claims] A plurality of rotors are slidably fitted into an annular cylinder chamber to form a plurality of working chambers within the cylinder chamber, and as the rotors rotate, the volumes of adjacent working chambers in the circumferential direction are opposite to each other. The rotors are interconnected so that the volume of each working chamber increases and decreases in a predetermined position in the circumferential direction of the cylinder chamber, and according to the rotation of the rotors. , an intake port on the peripheral wall of the cylinder chamber in relation to the position of increase/decrease in volume of the working chambers so that intake, compression, explosion, and exhaust operations are sequentially caused in the working chambers;
An ignition means and an exhaust port are provided so that the rotor is rotated in the circumferential direction of the cylinder chamber by the explosive action caused by the ignition of the ignition means synchronized with the rotation of the rotor, and the rotor is further provided at a central position of the cylinder chamber. A rotary internal combustion engine characterized in that each rotor is connected to an output shaft arranged so that the rotation of the rotor is extracted by the output shaft.