JP3941072B2 - Multi-chamber rotary engine - Google Patents

Description

  The present invention relates to a type of internal combustion engine that enables the use of a fuel for general internal combustion engines such as gasoline, which is a fossil fuel, and hydrogen, which is a non-polluting fuel.

The internal combustion engines currently in practical use include a 4-cycle reciprocating engine, a 2-cycle reciprocating engine, a Wankel type rotary engine, and the like, and the most popular engine is a 4-cycle reciprocating engine.
The 4-cycle reciprocating engine is currently used in many areas as the most complete and stable engine. However, the piston is in vertical motion, the intake and exhaust valves are also in linear motion, and is a source of engine noise. Due to the inertia of the exhaust valve mass, there is an upper limit of rotation, a part of the engine output is consumed for driving the valve, so the conversion efficiency from heat to kinetic energy is poor, and because of its structure, the complete combustion gas can be exhausted completely. There is a bottleneck such as the presence of residual gas in the combustion dome to reduce the oxygen content in the next intake stroke, the complicated structure, and the regular adjustment of the valve clearance.
The 2-cycle reciprocating engine is simpler and lighter than the 4-cycle reciprocating engine, but due to its structure, lubricating oil must be mixed with the fuel, and combustion oil combustion smoke is constantly generated in the exhaust gas. Since the blow-through of fuel occurs at low speed, the rotation is unstable, the generated torque in each rotation region is not flat, and as a result, there is a bottleneck such as a very poor fuel consumption rate.
The Wankel type rotary engine has a higher output than the 4-cycle reciprocating engine and has no intake / exhaust valve, so engine noise is very small. However, the compression ratio is fixed due to its structure, and the degree of freedom of change is high. The use of a flat spark plug with a flat tip causes a slight gap in the compression stroke, resulting in compression leakage and fuel blow-out, and unstable rotation during low-speed rotation. It is difficult and the combustion efficiency is low, so the fuel consumption rate is bad, the equilateral triangle rotor performs eccentric motion with respect to the output shaft, and undesirable vibration occurs, and the equilateral triangle rotor has eccentric motion. Airtight sealing between housings is difficult, and wear and thermal deformation are likely to occur due to surface friction, and there is a bottleneck such as low reliability and durability.

Although similar patents in the past have been devised and invented to avoid these bottlenecks, they are all completed to date due to imperfect structure, poor airtightness, inadequate response to thermal deformation, etc. Not reached.
Japanese Utility Model Publication No.59-142427 JP 58-200035 A Japanese Patent Laid-Open No. 01-313629 JP 05-340263 A Japanese Patent Laid-Open No. 06-280599 JP 09-158701 A

  The problem to be solved is to avoid almost all of the bottlenecks and imperfections of the prior art that each engine currently in practical use has.

  The present invention includes an elliptical or elliptical housing as a new engine structure, a true circular rotor coaxial with the output shaft, and a plurality of separators that divide the air chamber. A structure that ensures the airtightness of each of the air chambers divided by being forced to be in contact with the inner peripheral portion of the inner wall of the housing, regardless of the rotational position, and a structure that is mutually airtightly held by various airtight sealings, A structure in which the rotating round rotor is forcibly cooled with oil from the inside and the thickness of the separator as seen from the side of the housing is less than the screw diameter of a general flat spark plug as the engine becomes smaller. In order to prevent performance degradation due to blow-through, it is practical to use a spark plug with a new shape with a flat spark plug tip protruding. By making the hydrant hole small in diameter and ideally avoiding the blow-through that occurs when the separator passes through the spark plug, it is highly airtight and highly durable that conventional prior engines could not solve. The main feature is that no adjustment and improvement of the fuel consumption rate can be combined.

  The multi-chamber rotary engine according to the present invention improves the efficiency of conversion from heat to kinetic energy obtained by eliminating the valve mechanism, and prevents the generation of engine noise, and the upper limit of rotation. Improvement of the engine, elimination of adjustment points, and realization of an ideal intake / exhaust stroke, and the anti-smoke of the exhaust gas can be made without the need for mixing of lubricating oil when it is used in a two-cycle reciprocating engine. In addition, fuel blow-through does not occur, the generated torque is flat, and the fuel consumption rate is extremely good. Prevention, improvement of durability by maintaining an ideal airtight structure, improvement of fuel consumption rate decrease caused by structure such as compression leakage in flat spark plug part, It is a high output of the layers. Furthermore, it is possible to set an appropriate compression ratio and combustion temperature because it is possible to obtain a sufficient output without unnecessarily high compression ratio, and it has the effect of suppressing the generation of nitrogen oxides low, and also to a 4-cycle reciprocating engine. Has characteristics that it can be used for various fuels, such as hydrogen, which is a non-polluting non-polluting fuel.

  The purpose of avoiding almost all the bottlenecks of various existing engines is to achieve a small displacement with a multi-chamber rotary engine structure, a special hermetic sealing structure with excellent durability as a component, and a new-shaped spark plug Even in a simple structure, the structure that prevents the fuel consumption rate from dropping due to the blow through of the spark plug and the structure that forcedly cools the rotor from the inside are combined to reduce the failure rate due to the simple structure that eliminates the adjustment points. Also realized.

  The present invention relates to a kind of internal combustion engine that can use gasoline as a fossil fuel and other general internal combustion engine fuel as well as hydrogen as a pollution-free fuel. This is a room type rotary engine. The biggest bottleneck that could not be realized although the conventional similar preceding engine is conceptually realized is imperfect airtightness and accompanying reliability deterioration.

  In the first embodiment of the present invention as a means for avoiding these bottlenecks, an elliptical arc-shaped portion, an arc-shaped portion, and a straight portion are formed, and each curved portion and the straight portion are connected in an elliptical shape so that their tangent lines coincide with each other. It consists of an approximated housing, a perfect circular rotor coaxial with the output shaft, and a separator that divides the air chamber into four parts. The separator is provided at the inner periphery of the inner wall of the housing by the separator guide provided inside the housing regardless of the rotational position of the rotor. It has a structure that ensures the airtightness of each air chamber divided and forced to contact, and a structure in which each airtight seal is maintained by various airtight sealings, and the rotating true circular rotor is forcibly cooled with oil from the inside. If the structure and the thickness of the separator as seen from the side of the housing is smaller than the width of the spark plug mounting hole due to downsizing of the engine, a new shape Using a spark plug to prevent the spark plug portion from being blown through, the most important feature is that it has achieved both high airtightness and high durability that conventional prior engines could not solve. However, as an outstanding feature of performance obtained from this,

B: In the Wankel type rotary engine, because of its structure, the output shaft rotates 3 times during one rotation of the equilateral triangle rotor, and as a result, one explosion and expansion occurs per rotation of the output shaft, resulting in 4 cycles of 2 cylinders. Equivalent to a reciprocating engine, parallel operation of at least two rotors is necessary to obtain smooth rotation, and unnecessary vibrations generated by the eccentric rotation of the rotor, the housing and the equilateral triangle rotor Interfacial wear and airtightness decrease, and each apex of the equilateral triangle rotor is sharp, and the housing contacts only at one point when viewed from the side, so the airtightness generated by the gap generated when passing through the flat spark plug This reduction does not occur in the structure of the present invention, and a single rotor has sufficient performance. Therefore, reliability and durability are similar to reciprocating engines.
B: Since there is no intake / exhaust valve, the upper limit of rotation is not limited by the moment of inertia. The only rotation limitation is when the explosive combustion speed of the fuel used approaches the rotation speed of the true circular rotor, and the normal operating rotation range when using normal gasoline as a fuel is limited to the rotation limit of the reciprocating engine. When high performance fuel with much higher oxidizer added is used, it is possible to rotate at higher speed than that.
C: In the present invention, the number of divided air chambers can be selected to an arbitrary number of 3 or more. However, in the case of the multi-chamber rotary engine in which the air chamber is divided into four in the first embodiment of the present invention, the explosion expansion is performed four times during one rotation of the output shaft. Therefore, a smooth and quiet rotation equivalent to an 8-cylinder 4-cycle reciprocating engine can be obtained. Further, in the case of the multi-chamber rotary engine in which the air chamber is divided into six in the second embodiment of the present invention, six explosions and expansions are performed during one rotation of the output shaft, which is equivalent to a 12-cylinder four-cycle reciprocating engine. Smooth and quiet rotation.
D: Since there is no valve drive mechanism indispensable for a 4-cycle reciprocating engine, maintenance and inspection for maintaining performance are not required at all, and deterioration of engine performance over a long period is slight. As a result, the failure rate is reduced.
E: In the multi-chamber rotary engine with the air chamber divided into four in the first embodiment of the present invention, when the displacement is the same as that of the 8-cylinder 4-cycle reciprocating engine, an output of about 8 times is obtained at the same rotation, and more The computational output is even higher because it has a higher high-speed service rotation range. In other words, the engine performance is better than that of an 8-cylinder, 4-cycle reciprocating engine with 1/8 displacement and 1/8 engine weight ratio. Similarly, in the multi-chamber rotary engine in which the air chamber is divided into six in the second embodiment of the present invention, when the displacement is the same as that of the 12-cylinder four-cycle reciprocating engine, an output of about 12 times is obtained at the same rotation, The computational output is even higher because it has a much higher speed of normal use rotation. In other words, with a displacement of 1/12 and an engine weight ratio of 1/12, a performance superior to that of a 12-cylinder 4-cycle reciprocating engine can be obtained.
F: Since the engine weight can be significantly reduced as compared with an 8- or 12-cylinder 4-cycle reciprocating engine that obtains the same output, a dramatic improvement in fuel efficiency can be achieved as a comprehensive result when mounted on a passenger car or the like.
G: Although the compression ratio can be changed by changing the shape of the housing approximate to an ellipse with respect to the true circular rotor, in the case of the multi-chamber rotary engine in which the air chamber according to the present invention is divided into four, the smooth rotation is ensured. As a result of suppressing the generation of nitrogen oxides by reducing the combustion temperature by setting the optimum compression ratio when the emphasis is taken to about 6 or so, it has features such as being able to reduce pollution. In the case of the multi-chamber type rotary engine in which the air chamber is divided into six in the second embodiment of the present invention, the compression efficiency can be increased to about 10 or more, so that the combustion efficiency is further improved. The engine is cooled by either air cooling or liquid cooling, which is an existing technology, and fuel injection is performed by either a carburetor or a fuel injection device, which is an existing technology. Furthermore, by using a spark plug with a new shape and making the spark plug hole small in diameter to prevent the spark plug from being blown through, it can be applied to small displacement rotary engines that were not suitable for conventional Wankel type rotary engines. .

  In the multi-chamber type rotary engine having the four-split air chamber according to the first embodiment of the present invention, the distance between the inner walls of the housing is 35.5 when the diameter of the true circular rotor is 100 millimeters and the elliptical portion of the elliptical housing is 140 millimeters. The maximum intake volume is 50 CC, the minimum compression volume is 7.9 CC, and the compression ratio is 6.33.

  FIG. 1 is a front perspective view of Embodiment 1 of the present invention. H01 is a main housing, in which an intake port of H04 and an exhaust port of H05 are positioned symmetrically with respect to the vertical line, and an oil injection port of H08 and an oil discharge port of H09 are positioned above and below the side surface, A new shaped spark plug of P01 is located. R01 is a true-circular rotor and is located at substantially the center position of the main housing of H01, but the lower part is in contact with the main housing of H01 through the airtight sealing of H07, and the upper part is non-contact with a gap. . In the drawing, it is assumed that the true circular rotor R01 rotates clockwise. The separators of S01 are disposed at a relative angle of 90 degrees with respect to the center position, and are sandwiched between the R01 true circular rotors and rotate together. However, the positions of the separators by the H06 separator guide fixed to the housing portion. Shifts with the rotation angle, and the separator tip portion of S01 is always forcedly brought into contact with the inner peripheral portion of the inner wall of the main housing of H01. In the separator position in the figure, A01 air chamber 1 indicates the maximum volume state of the intake stroke and the end stage of the intake stroke, A02 air chamber 2 indicates the maximum compression state of the compression stroke and the start stroke of the ignition explosion, and A03 The air chamber 3 shows a maximum volume state of an explosion / expansion stroke and an exhaust stroke start stage.

  FIG. 2 is a side cross-sectional view of the first embodiment of the present invention. The side wall housing 1 of H02 and the side wall housing 2 of H03 have the same shape, and the main housing of H01 is sandwiched from both sides to form a housing portion surrounding the R01 round rotor. R02 is an output shaft, and outputs the rotational output obtained by the true circular rotor of R01 to the outside. G01 is a hermetic seal 1, and is positioned so as to fit together into a groove carved in the inner periphery of the R01 round rotor divided into four parts and a groove carved in the side wall housings of H02 and H03. In addition, the round rotor side surface of R01 and the housing side wall surfaces have a slight gap and are not in surface contact.

  FIG. 3 is a detailed view of the separator in Example 1 of the present invention. The separator of S01 has grooves on the upper surface and side surfaces, and its lateral width substantially matches the width of the main housing of H01, but is slightly narrower. The hermetic seal 3 of G03 and the hermetic seal 4 of G04 are exactly the same, but are overlapped and positioned symmetrically when incorporated in the separator of S01. The spring 1 of SP1 and the spring 2 of SP2 are the same, and are positioned in the hole carved in S01 so as to push the hermetic sealing 3 of G03 and the hermetic sealing 4 of G04 upward through the auxiliary hermetic sealing 2 of G06. Function. The wave spring 1 of SP3 pushes the hermetic seal 3 of G03 and the hermetic seal 4 of G04 in the left-right direction through the auxiliary hermetic seal 1 of G05 that moves up and down together with the hermetic seal 3 of G03 and the hermetic seal 4 of G04. To function. The separator of S01 is forcibly moved by the rotational position of the true circular rotor of R01 and forcibly positioned by the separator guide arranged in the housing portion, but a slight error occurs at this time. In order to compensate for this slight error and always ensure a certain degree of tightness, the G03 hermetic seal 3 and the G04 hermetic seal 4 and their associated structures are indispensable elements.

  FIG. 4 is a detailed view of the rotor part hermetic sealing in Example 1 of the present invention. Each of the four divided rotor parts has a hermetic sealing groove in the periphery, and two G01 hermetic sealings 1 and two G02 hermetic sealings 2 enter this groove and surround four surrounding surfaces. Furthermore, the respective hermetic seals overlap each other to ensure a further tightness. The surface in contact with the separator of S01 inserted between the adjacent divided rotor portions has an SP4 wave spring 2 inside, and this pressure ensures airtightness. The portion in contact with the side wall surface of the housing portion is appropriately pressed out to the side surface of the housing by the SP5 wave spring 3 provided inside and protrudes beyond the width of the R01 true circular rotor. By entering the provided sealing groove, further airtightness on the side surface is ensured.

  FIG. 5 is a detailed view of the spark plug having a new shape according to the first embodiment of the present invention. The P01 spark plug has a new P011 center electrode, a P012 insulator, and a P013 external electrode. The P013 external electrode recedes from the P011 center electrode and the P012 insulator tip. As a result of the discharge ignition function performed together with the inner wall of the H01 housing by the projecting portion involved in the discharge ignition, the spark plug hole provided in the H01 housing is substantially reduced in diameter, and the spark plug site generated when applied to a small engine Prevents blow-through phenomenon that occurs in

  FIG. 6 is a detailed view of the main part of the housing according to the first embodiment of the present invention. The main housing of H01 is provided with an H04 air inlet and an H05 air outlet symmetrically, which are connected and integrated by a slit of H15. H13 is an airtight sealing groove 2.

  FIG. 7 is a detailed view of the side surface of the housing according to the first embodiment of the present invention. The side wall housing 1 of H02 and the side wall housing 2 of H03 have the same shape, and a housing portion is formed by sandwiching the main housing of H01 from both sides. H02 side wall housing 1 has H06 separator guide, H08 oil inlet, H09 oil outlet, H10 airtight sealing groove 1, H11 negative pressure relief groove, H12 pressure relief groove, H13 airtight sealing groove 2, H14 output bearings are provided.

  FIG. 8 is a detailed view of a true circular rotor portion in Embodiment 1 of the present invention. As shown in the figure, R01's true circular rotor is divided into four blocks. R02 is an output shaft, R03 is an air chamber surface, R04 is an air chamber surface support portion, and R05 is a separator holding portion. The figure below shows the internal state in a state where the true circular rotor of R01 is rotated 45 degrees, and the side view shows the insertion state of the airtight sealings G01 and G02 for hermetically sealing each rotor air chamber.

  The first embodiment of the present invention is a multi-chamber type rotary engine in which a housing shape constituted by a multi-curved surface shape and an air chamber are divided into four, but the second embodiment is a multi-chamber chamber in which the housing shape is a perfect ellipse and the number of divisions is six. Although it is a type rotary engine, its structure is slightly complicated, but a higher compression ratio can be realized, and as a result, the displacement to output ratio is improved.

  In the multi-chamber type rotary engine having the six-part air chamber of the second embodiment, the diameter of the true circular rotor is 100 mm, the ellipse of the elliptical housing is 140 mm in order to share the components in the first embodiment. The maximum intake volume is 34.3 CC and the minimum compression volume is 2.92 CC when the inner wall distance of the housing is 35.5 millimeters and the main dimensions in Example 1 are the same, and a compression ratio of 11.75 is obtained. .

  FIG. 9 is a front perspective view of the second embodiment of the present invention. H01B is a main housing. H04B intake port, H05B exhaust port and H08B oil injection port and H09B oil discharge port are located at the upper and lower positions at symmetrical positions with respect to the vertical line. A new shaped spark plug is located. R01B is a true circular rotor, which is located at substantially the center position of the main housing of H01B, but the lower part is in contact with the main housing of H01B through the hermetic sealing of H07B, and the upper part is non-contact with a gap. . In the figure, it is assumed that the R01B true circular rotor rotates clockwise. The separators of S01B are arranged at a relative angle of 60 degrees with respect to the center position. The position angle changes with the rotation of the R01B true circular rotor, and the separator guide of H06B fixed to the housing portion causes the S01B separator guide. The separator tip is always forcibly contacted with the inner peripheral part of the inner wall of the main housing of H01B. The separator of S01B is the same as that of S01, and various hermetic seals and wave springs used for the rotor are similar to those of the first embodiment.

  FIG. 10 is a side view of a housing and a rotor in Example 2 of the present invention. The basic structure of the housing is almost the same as that of the first embodiment, but the H06B separator guide shape and the shape of the intake / exhaust portion are largely different, but in the second embodiment, the air chamber which is not involved in the operation is the second embodiment. Since there are more than one, the negative pressure and pressurization relief grooves generated at that portion are widened.

  An arbitrary compression ratio can be basically obtained by changing the housing shape of the multi-chamber rotary engine in which the air chamber is divided into four in the first embodiment of the present invention. An example of a diesel engine that uses diesel oil as fuel is shown. For mutual comparison and sharing of parts, the diameter of the perfect rotor is 100 mm, the elliptical shape of the oval housing is 140 mm, and the inner wall distance of the housing is 35.5 mm. However, the housing shape is greatly changed. In the third embodiment, the maximum intake volume is 47.67 CC, and the minimum compression volume is 2.25 CC, and a high compression ratio of 21.21 is obtained.

  FIG. 11 is a front perspective view of the third embodiment of the present invention. H01C is a main housing, where an H04C intake port, an H05C exhaust port, and an H08C oil injection port and an H09C oil discharge port are positioned vertically and symmetrically with respect to the vertical line, and P01C A fuel injector is located. R01C is a true circular rotor and is located at the center position of the main housing of H01C, but the lower part is in contact with the main housing of H01C through the airtight sealing of H07C, and the upper part has a concentric space and is non-contacting is there. In the figure, it is assumed that the R01C true circular rotor rotates clockwise. The S01C separators are arranged at a relative angle of 90 degrees with respect to the center position. The position angle changes with the rotation of the R01C true circular rotor, and the S06C separator guide is fixed to the housing portion by the H06C separator guide. The separator tip is always forced to contact the inner peripheral part of the inner wall of the main housing of H01C. The separator of S01C is the same as that of S01, and various hermetic seals and wave springs used for the rotor are similar to those of the first embodiment.

  FIG. 12 is a side view of a housing and a rotor in Example 3 of the present invention. The basic structure of the housing is partly different from the other embodiments, but there are deviation points where the tangents of the curves are not the same in the two parts, but these parts are connected by a smooth curve. Along with this, the separator guide shape of H06C is considerably deformed. Due to this deviation point, the occurrence of moment friction in the separator cannot be ignored compared to the other examples, so that it is necessary to give an appropriate limit to the upper limit of rotation.

  Example 4 considers the displacement suitable for a general-purpose engine. The diameter of the true circular rotor is 160 mm, the elliptical housing is 224 mm, the maximum intake volume is 333.3 CC, and the minimum compression volume is 44. .404CC and a compression ratio of 7.504. The major changes associated with this increase in size are that the shape of the intake and compression combustion chambers has curved transitions to improve compression combustion efficiency, double the airtight sealing of the true circular rotor, Increased thickness of the separator as seen and made three independent airtight seals, widened the thickness of the separator, which allowed the use of general flat spark plugs, parallel spacing of the housing In order to make the combustion diffusion distribution uniform at the time of high speed rotation, two general flat spark plugs are used.

  FIG. 13 is a front perspective view of Embodiment 4 of the present invention. The basic part is basically the same as FIG. 1, H01D is a main housing, H08D intake port and H05D exhaust port, and H08D oil injection port and H09D oil discharge port are located above and below the side, The general flat spark plug of P01D is located in the center. R01D is a true-circular rotor, which is located at substantially the center position of the main housing of H01D, but the lower part is in contact with the main housing of H01D through the hermetic sealing of H07D, and the upper part is non-contact. In the figure, it is assumed that the R01D true circular rotor rotates clockwise. The S01D separators are arranged at a relative angle of 90 degrees with respect to the center position, and rotate together with being sandwiched between R01D true circular rotors. However, the position of the separator is fixed by the H06D separator guide fixed to the housing part. Shifts with the rotation angle, and the separator tip of S01D is always forced to contact the inner peripheral part of the inner wall of the main housing of H01D.

  FIG. 14 is a side view of the housing according to the fourth embodiment of the present invention. The side wall housing 1 of H02D and the side wall housing 2 of H03D have a mirror image symmetrical shape, and form a housing portion by sandwiching the main housing of H01D from both sides. Both side wall housings are equipped with H06D separator guide, H08D oil inlet, H09D oil outlet, H11D negative pressure relief groove, H12D pressure relief groove, and H14D output bearing. As a part different from the example, in addition to the hermetic sealing groove 1 of H10D, a further hermetic sealing groove 3 of H15D is provided, and the hermetic sealing on both sides of the housing and the rotor is doubled.

  FIG. 15 is a side sectional view of Embodiment 4 of the present invention. The side wall housing 1 of the H02D and the side wall housing 2 of the H03D have a mirror image symmetrical shape, and form a housing portion surrounding the R01D true circular rotor by sandwiching the main housing of the H01D from both sides. R02D is an output shaft, and outputs the rotational output obtained by the R01D true circular rotor to the outside. The G01D airtight seal 1 and the G02D airtight seal 2 are a pair of combined airtight seals. The G01D airtight seal 6 consists of a G07D airtight seal 6 and a G08D airtight seal 7 at a slightly smaller concentric position. The groove is carved into the groove carved in the inner periphery of the R01D round rotor divided into four parts and the groove carved into the side wall housings of H02D and H03D. Incidentally, the side surface of the round rotor of R01 and the wall surfaces on both sides of the housing portion have a slight gap and are not in surface contact. In Example 4, two general flat spark plugs are used in consideration of the combustion diffusion distribution at the time of high-speed rotation because the parallel interval of the housing is widened, and this relative positional relationship is also shown.

  FIG. 16 is a detailed view of a separator in Example 4 of the present invention. The major difference from the separator detailed view of FIG. 3 is not an arrangement in which the hermetic seals are overlapped with each other, but the completely same G03D hermetic seals 3 are arranged on the left and right on the same line, and the form is one sheet. As a result of mounting a set of two sheets in three sealing grooves provided independently, three layers of independent hermetic sealing are formed. Accordingly, the spring SP1D and the auxiliary hermetic sealing G06D are changed from a true circular spring to an oval spring.

  It belongs to a kind of new rotary engine, and by ensuring the airtightness of each part, it has achieved both innovative high performance and higher reliability than the existing Wankel type rotary engine, and as a result, performance is not impaired. As a comprehensive result when used in passenger cars, etc., the fuel consumption rate has been further improved, and the combustion temperature management by setting an arbitrary compression rate has been reduced. It is possible to use hydrogen, which is a pollutant fuel, and from small applications such as small agricultural equipment, small generators, small outboard motors, and small motorcycles that were not suitable for existing Wankel rotary engines to aircraft. It has become possible to handle a wide variety of uses up to the application.

It is a front perspective view in Example 1 of the present invention. It is side surface sectional drawing in Example 1 of this invention. It is a separator detail drawing in Example 1 of this invention. It is a rotor part airtight sealing detailed drawing in Example 1 of this invention. It is sectional drawing of the spark plug part of the new shape in Example 1 of this invention. It is a housing main part detail drawing in Example 1 of this invention. It is a housing side part detail drawing in Example 1 of this invention. It is a detailed view of a true circular rotor part in Example 1 of the present invention. It is a front perspective view in Example 2 of the present invention. It is a housing side part and rotor side view in Example 2 of this invention. It is a front perspective view in Example 3 of the present invention. It is a housing side part and rotor side view in Example 3 of this invention. It is a front perspective view in Example 4 of the present invention. It is a housing side view in Example 4 of the present invention. It is side surface sectional drawing in Example 4 of this invention. It is a separator detail drawing in Example 4 of this invention.

Explanation of symbols

A01 Air chamber 1
A02 Air chamber 2
A03 Air chamber 3
G01 Airtight sealing 1
G02 Airtight sealing 2
G03 Airtight sealing 3
G04 Airtight sealing 4
G05 Auxiliary airtight sealing 1
G06 Auxiliary airtight sealing 2
H01 Main housing H02 Side wall housing 1
H03 Side wall housing 2
H04 Intake port H05 Exhaust port H06 Separator guide H07 Airtight sealing 5
H08 Oil inlet H09 Oil outlet H10 Airtight sealing groove 1
H11 Negative pressure relief groove H12 Pressure relief groove H13 Airtight sealing groove 2
H14 Output bearing P01 Spark plug of new shape P011 Center electrode P012 Insulator P013 External electrode R01 True circular rotor R02 Output shaft R03 Air chamber surface R04 Air chamber surface support portion R05 Separator holding portion S01 Separator SP1 Spring 1
SP2 Spring 2
SP3 Wave spring 1
SP4 wave spring 2
SP5 Wave spring 3
H01B Main housing H02B Side wall housing 1
H03B Side wall housing 2
H04B Intake port H05B Exhaust port H06B Separator guide H07B Airtight sealing 5
H08B Oil inlet H09B Oil outlet H10B Airtight sealing groove 1
H11B Negative pressure relief groove H12B Pressure relief groove H13B Airtight sealing groove 2
H14B Output bearing P01B Newly shaped spark plug R01B True circular rotor R02B Output shaft R05B Separator holder S01B Separator H01C Main housing H02C Side wall housing 1
H03C Side wall housing 2
H04C Air inlet H05C Air outlet H06C Separator guide H07C Airtight sealing 5
H08C Oil inlet H09C Oil outlet H10C Airtight sealing groove 1
H11C Negative pressure relief groove H12C Pressure relief groove H13C Airtight sealing groove 2
H14C Output bearing P01C Fuel injection device R01C True circular rotor R02C Output shaft R05C Separator holder S01C Separator G01D Airtight sealing 1
G02D Airtight sealing 2
G03D Airtight sealing 3
G05D Auxiliary airtight sealing 1
G06D Auxiliary airtight sealing 2
G07D Airtight sealing 6
G08D Airtight sealing 7
H01D Main housing H02D Side wall housing 1
H03D Side wall housing 2
H04D Air inlet H05D Air outlet H06D Separator guide H07D Airtight sealing 5
H08D Oil inlet H09D Oil outlet H10D Airtight sealing groove 1
H11D Negative pressure relief groove H12D Pressure relief groove H13D Airtight sealing groove 2
H14D output bearing H15D airtight sealing groove 3
P01D General flat spark plug R01D True circular rotor R02D Output shaft S01D Separator SP1D Spring 1
SP3D wave spring 1

Claims (4)

When the fuel is supplied by the fuel injection device in addition to the intake port and the spark plug hole, the fuel injection port and the fuel injection port are provided. A housing having an exhaust port, a perfectly circular rotor that is positioned inside and rotates coaxially with the output shaft, and has a hollow structure and is lubricated and forcedly cooled by oil, and a perfectly circular rotor And a plurality of separators that divide the space formed by the housing and the true circular rotor into at least three or more closed air chambers, and the inner peripheral portion of the inner wall of the housing and the true circular rotor are By having a structure in which the intake air chamber and the exhaust air chamber are separated from each other by being arranged so as to be in surface contact at one point of the portion sandwiched between the intake port and the exhaust port, Each worker There appeared simultaneously in the output shaft 1 rotating, the internal combustion engine proceeds,
In the true circular rotor (R01), one piece is L-shaped when viewed from the inner periphery of the main housing (H01), and four arc-shaped hermetic seals (G01 and G02) are viewed from the side of the housing. The airtight sealing (G01 and G02) is fitted and pressed into the airtight sealing groove 1 (H10) provided in the both side wall housings (H02 and H03), and is in surface pressure contact with the separator (S01). Each piece has a portion overlapping each other, and a wave-shaped spring (SP4 and SP5) is inserted into a sealing groove carved so as to surround the four sides of each of the round rotors (R01) divided by the separator (S01). A multi-chamber rotary engine comprising one or more hermetic sealing structures that are inserted and arranged concentrically with respect to the output shaft.   The multi-chamber rotary engine according to claim 1, wherein the separator (S01) is rotated by a true circular rotor (R01) by a separator guide (H06) fixed inside the plane-symmetric side wall housings (H02 and H03). Regardless of the position, the air chamber is forcibly positioned so as to be close to the inner periphery of the housing at one point when viewed from the side surface of the housing. The inner wall of the housing has a slight gap to prevent restriction due to thermal expansion. This separator (S01) is independent between the side wall of the housing and the separator and between the inner wall of the housing inner wall and the separator. An airtight sealing groove for providing an airtight sealing that closes at a plurality of pressure contact surfaces is provided, and the groove has at least two or more. A plurality of character-shaped hermetic seals (G03 and G04) are arranged in a state of being symmetrically overlapped with each other, or a left-right symmetric L-shaped hermetic seal (G03D) having a portion overlapping on a mating surface is arranged in a straight line. A plurality of hermetic sealing members are arranged, and each is pressed against the inner peripheral surface of the main housing (H01) by circular or oval springs (SP1 and SP2), and at the same time, both side wall housings by wave springs (SP3). A multi-chamber rotary engine having a structure in which each air chamber is closed and sealed by being pressed against each other (H02 and H03).   In the L-shaped hermetic seal (G03 and G04) equipped in the separator according to claim 2, the wave spring (SP3) for press-contacting the L-shaped hermetic seal (G03 and G04) to the side of the housing and the separator An additional auxiliary seal (G05) that moves in position with the L-shaped hermetic seal (G03 and G04) is provided between the hermetic seal grooves, and the L-shaped hermetic seal (G03 and G04) is pressed against the inner periphery of the housing. A multi-chamber rotary engine having a structure in which a circular or oval auxiliary seal (G06) is provided between a circular or oval spring (SP1 and SP2) and an L-shaped hermetic seal (G03 and G04).   The multi-chamber rotary engine according to any one of claims 1 to 3, wherein only the discharge tip portion (P011) of the central electrode involved in discharge ignition and the surrounding insulator portion (P012) are protruded. A multi-chamber rotary engine having a spark plug structure (P01) in which the housing portion of the engine takes on the function of the surrounding discharge electrode part (P013) when the engine is mounted.

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