JP2013060811A - Rotary internal combustion engine - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a rotary internal combustion engine configured of simple components with little vibration and high productivity at low cost.SOLUTION: This rotary internal combustion engine includes: a rotor housing (1) comprising a main rotor chamber (7) including an inner peripheral surface formed in a cylindrical surface (7a), and two sub rotor chambers (8, 9) arranged on both sides across the main rotor chamber (7) and including inner peripheral surfaces formed in cylindrical surfaces (8a, 9a) having smaller diameters than the cylindrical surface (7a) of the main rotor chamber (7); a main rotor (15) which is rotatably and pivotally supported by the rotor housing (1) to be close contact with the inner peripheral surface of the main rotor chamber (7) and has a side surface formed in a convex lens shape; and sub rotors (16, 17) which are rotatably and pivotally supported by the rotary housing (1), in close contact with each of the inner peripheral surfaces of the two sub rotor chambers (8, 9), and have side surfaces having a convex lens shape.

Description

  The present invention relates to a rotary internal combustion engine in which a member that changes the volume of a combustion chamber rotates without reciprocating and converts chemical energy held by fuel into mechanical energy.

  The internal combustion engine mounted on the body of a four-wheeled vehicle called a motorcycle or a normal vehicle has a relatively simple structure, good sealing performance, and relatively good fuel consumption compared to other types of internal combustion engines. A reciprocating internal combustion engine in which a piston that changes the volume of the combustion chamber reciprocates has been widely used.

  However, in a reciprocating internal combustion engine, vibration due to the reciprocating motion of the piston is generated. Therefore, as an internal combustion engine that reduces this vibration and further reduces the size and output, the rotor housing having a two-node peritrochoidal curve on the inner peripheral surface is used. A Wankel type rotary internal combustion engine has been developed in which a substantially triangular rotor having a centrally bent side outwardly rotates.

  In this Wankel type rotary internal combustion engine, since the rotor is accompanied by planetary motion, reciprocal vibration is generated, and it is difficult to sufficiently reduce the vibration, and the shape of the rotor housing and the rotor is complicated, and the rotor is driven. The transmission mechanism was complicated.

  As an internal combustion engine to be improved, there is a rotary internal combustion engine in which the rotor does not perform planetary motion and rotates at one place (see Japanese Patent Application Laid-Open No. 2005-315205).

Japanese Patent Laying-Open No. 2005-315205

  In the rotary internal combustion engine described in Patent Document 1, since the planar shape of the rotor is complicated, processing is difficult, productivity is low, and cost is unavoidable.

  The present invention relates to an improvement of a rotary internal combustion engine that overcomes such difficulties, and an object thereof is to provide a rotary internal combustion engine that is configured with simple-shaped parts, that has less vibration, has high productivity, and is low in cost. It is said.

In order to achieve the above object, the invention according to claim 1
One main rotor chamber having an inner peripheral surface formed in a cylindrical surface, and disposed on both sides of the main rotor chamber, and the inner peripheral surface is formed in a cylindrical surface having a smaller diameter than the cylindrical surface of the main rotor chamber. A rotor housing formed with two sub-rotor chambers;
A main rotor having a convex lens-like shape on the side surface of the main rotor pivotally supported in the rotor housing in a state of being in close contact with the inner peripheral surface of the main rotor chamber;
A sub-rotor having a convex lens-like shape on the side surface of the sub-rotor pivotably supported by the rotor housing in close contact with the inner peripheral surfaces of the two sub-rotor chambers;
An intake port communicating with one of the two sub-rotor chambers, or a part of one main rotor chamber adjacent to the one sub-rotor chamber;
An exhaust port communicating with one of the two sub-rotors, or a portion of the other main rotor chamber adjacent to the one sub-rotor chamber;
A combustion chamber formed in the other sub-rotor chamber of the two sub-rotor chambers;
The one main rotor and the two sub-rotors are all connected in the same direction so as to be rotatable at the same rotational speed, and are configured by a power transmission mechanism that extracts power from the rotation shaft of the main rotor. This is a featured rotary internal combustion engine.

The invention according to claim 2
The diameter of the circumferential surface of the main rotor chamber and the large diameter of the main rotor are R,
The diameter of the circumferential surface of the sub-rotor chamber and the large diameter of the sub-rotor are r,
Ra, ra, the small diameter of the main rotor and sub-rotor
When the distance between the rotation center of the main rotor and the rotation center of the sub-rotor is L,
L ² = R ² + r ² (1)
R + ra = Ra + r (2)
The rotary internal combustion engine according to claim 1, wherein:

The invention described in claim 3
The main rotor is directed from the center of the main rotor toward the small diameter portion, and is centered at a location separated by a distance corresponding to the large diameter of the sub rotor.
Formed in a shape along a cylindrical surface of radius L,
The sub-rotor is directed from the center of the sub-rotor to the small diameter portion,
Centered at a location separated by a distance corresponding to the large diameter of the main rotor,
The rotary internal combustion engine according to claim 2, wherein the rotary internal combustion engine is formed in a shape along a cylindrical surface having a radius L.

The invention according to claim 4
The rotary according to any one of claims 1 to 3, wherein the opening of the intake port and the opening of the exhaust port are respectively formed on a peripheral wall of the main rotor chamber adjacent to the sub-rotor chamber on the intake / exhaust side. It is an internal combustion engine.

The invention according to claim 5
The opening of the exhaust port is formed on the side wall of the main rotor chamber adjacent to the one sub-rotor chamber where the intake / exhaust port is disposed, and the opening of the intake port is formed on the side wall of the side surface of the one sub-rotor chamber. 4. The rotary internal combustion engine according to claim 1, wherein the rotary internal combustion engine is formed.

The invention described in claim 6
The water injection valve for performing water injection on the downstream side of the sub-rotor in the other sub-rotor chamber is provided for the spark plug provided in the other sub-rotor chamber in which the combustion chamber is formed. A rotary internal combustion engine according to any one of claims 1 to 5.

  According to the first aspect of the present invention, since not only the reciprocating motion part but also the eccentric rotation part is eliminated, the vibration of the internal combustion engine can be further reduced and the friction can be reduced. Miniaturization can be achieved.

  According to the second aspect of the present invention, the inner peripheral surfaces of the main rotor chamber and the sub-rotor chamber are formed in a cylindrical surface, and the outer peripheral surfaces of the main rotor and the sub-rotor are formed in a cylindrical surface having a constant curvature radius. It is possible to improve the productivity by simplifying the shape of the components.

  According to the third aspect of the present invention, the outer peripheral surface of the main rotor is formed into a cylindrical surface having a required radius R by using a jig that turns around a predetermined distance from the main rotor and the sub-rotor. It is very easy to process, and the sub-rotor can be processed very easily as well.

  According to the invention described in claim 4, the intake and exhaust timing and the opening period can be freely changed, and the performance and characteristics of the internal combustion engine can be improved.

  According to the fifth aspect of the present invention, it is possible to increase the charging efficiency by expanding the timing of overlap of intake and exhaust, and to improve the performance of the internal combustion engine.

  According to the sixth aspect of the present invention, when the in-cylinder cooling performance is improved by the latent heat of vaporization and the fuel efficiency is improved by the steam pressure, the injection steam is blocked by the sub-rotor and the spark plug is prevented from getting wet, and the water injection timing And the degree of freedom of the position of the spark plug is improved.

It is explanatory drawing which illustrated the basic schematic structure of the rotary internal combustion engine of this invention. It is explanatory drawing of FIG. 1, and is explanatory drawing of the state which rotated the rotation position of the main rotor and the subrotor 90 degrees. It is explanatory drawing explaining that both rotors can always maintain a contact state irrespective of what rotation position a main rotor and a subrotor have. At the boundary point P ₁ of the main rotor chamber and Saburota chamber, the large diameter portion of the large-diameter portion and Saburota of the main rotor abuts each other, and a line segment connecting the center and the boundary point of the main rotor chamber, the center of Saburota chamber It is explanatory drawing which shows that the included angle with the line segment which connects and a boundary point is a right angle. In the internal combustion engine shown in FIG. 4, the diameter of the main rotor chamber is made smaller than that shown in FIG. 4 without changing the inter-axis distance connecting the center of the main rotor chamber and the center of the sub-rotor chamber. Even when the diameter is increased, the large diameter portion of the main rotor and the large diameter portion of the sub-rotor are in contact with each other, and the line segment connecting the center of the main rotor chamber and the boundary point is connected to the center of the sub-rotor chamber and the boundary point. It is explanatory drawing which shows that the included angle with a line segment is a right angle. In the internal combustion engine shown in FIG. 4, the diameter of the main rotor chamber is made larger than that shown in FIG. 4 without changing the inter-axis distance connecting the center of the main rotor chamber and the center of the sub-rotor chamber. Even when the diameter is reduced, the large diameter portion of the main rotor and the large diameter portion of the sub-rotor are in contact with each other, and the line segment connecting the center of the main rotor chamber and the boundary point is connected to the center of the sub-rotor chamber and the boundary point. It is explanatory drawing which shows that the included angle with a line segment is a right angle. 1 is a front view of a first embodiment of an internal combustion engine of the present invention. 1 is a right side view of a first embodiment of an internal combustion engine of the present invention. It is the perspective view which looked at the 1st example of the internal-combustion engine of the present invention from the slanting right back. It is the exploded view which looked at the 1st example of the internal-combustion engine of the present invention from diagonally right back. In the first embodiment of the internal combustion engine of the present invention, in order to illustrate the operation state, the state where the large diameter portion of the main rotor is in contact with the small diameter portion of the sub rotor as viewed from the rear is illustrated. It is a rear view. FIG. 12 is a rear view illustrating a state in which the main rotor and the sub rotor are rotated about 45 ° clockwise from the state illustrated in FIG. 11. FIG. 13 is a rear view illustrating a state in which the main rotor and the sub-rotor are further rotated by about 45 ° clockwise compared to FIG. 11 from the state illustrated in FIG. 12. FIG. 14 is a rear view illustrating a state in which the main rotor and the sub-rotor are further rotated by about 135 ° clockwise from the state illustrated in FIG. 13 in comparison with FIG. FIG. 14 is a rear view illustrating a state in which the main rotor and the sub-rotor are further rotated from the state illustrated in FIG. 14, and both large diameter portions of the main rotor and the sub-rotor are in contact with each other at the boundary point between the main rotor chamber and the sub-rotor chamber. It is. FIG. 16 is a rear view illustrating a state in which the main rotor and the sub rotor are further rotated from the state illustrated in FIG. 15 and the large diameter portion of the main rotor is in contact with the small diameter portion of the sub rotor. FIG. 17 is a rear view illustrating a state in which the main rotor and the sub rotor are rotated about 45 ° clockwise from the state illustrated in FIG. 16. FIG. 18 is a rear view illustrating a state in which the main rotor and the sub rotor are further rotated about 45 ° clockwise from the state illustrated in FIG. 17. FIG. 19 is a rear view illustrating a state in which the main rotor and the sub rotor are further rotated by about 45 ° from the state illustrated in FIG. 18. FIG. 19 shows a state in which the main rotor and the sub-rotor are further rotated, and the large-diameter portions of the main rotor and the sub-rotor are in contact with each other at the boundary between the main rotor chamber and the sub-rotor chamber. FIG. In the second embodiment of the present invention, in order to illustrate the operation state, a rear view illustrating a state in which the large diameter portion of the sub rotor is in contact with the small diameter portion of the main rotor when the main rotor and the sub rotor are viewed from the rear. is there. It is the disassembled perspective view which looked at 2nd Example in the state illustrated in FIG. 21 from diagonally right back. FIG. 23 is an exploded perspective view illustrating a state in which the main rotor and the sub-rotor are rotated about 45 ° clockwise from the state illustrated in FIG. 22. FIG. 25 shows a state in which the main rotor and the sub-rotor are further rotated clockwise from the state shown in FIG. 25 and both large diameter portions of the main rotor and the sub-rotor are in contact with each other at the boundary point between the main rotor chamber and the sub-rotor chamber. It is a disassembled perspective view. FIG. 25 is an exploded perspective view illustrating a state in which the main rotor and the sub rotor are further rotated clockwise from the state illustrated in FIG. 24 and the large diameter portion of the main rotor is in contact with the small diameter portion of the sub rotor. FIG. 25 shows a state in which the main rotor and the sub-rotor further rotate in the clockwise direction from the state shown in FIG. 25, and the large diameter portions of the main rotor and the sub-rotor contact each other at the boundary point between the main rotor chamber and the sub-rotor chamber. FIG. FIG. 27 is an exploded perspective view illustrating a state in which the main rotor and the sub rotor are further rotated clockwise from the state illustrated in FIG. 26. FIG. 28 is an exploded perspective view illustrating a state in which the main rotor and the sub rotor are further rotated clockwise from the state illustrated in FIG. 27 and the large diameter portion of the sub rotor is in contact with the small diameter portion of the main rotor. 28 is a disassembled state in which the main rotor and the sub-rotor further rotate in the clockwise direction from the state illustrated in FIG. 28 and the large-diameter portions of the main rotor and the sub-rotor are in contact with each other at the boundary point between the main rotor chamber and the sub-rotor chamber. It is a perspective view. FIG. 30 is an exploded perspective view illustrating a state in which the main rotor and the sub-rotor further rotate in the clockwise direction from the state illustrated in FIG. 29 and are in contact with each other at the boundary point between the main rotor chamber and the sub-rotor chamber.

  Hereinafter, an embodiment of the rotary internal combustion engine 0 according to the present invention shown in FIGS. 1 to 15 will be described.

  Hereinafter, in the specification of the present application, the top, bottom, front, back, left and right of the rotary internal combustion engine 0 are the same as the top, bottom, front, back, left and right directions of the vehicle on which the rotary internal combustion engine 0 is mounted.

  First, a basic schematic structure of a rotary internal combustion engine 0 according to the present invention will be described with reference to FIGS. 1 and 2.

  The rotor housing 1 of the rotary internal combustion engine 0 includes a main rotor chamber 7 having an inner peripheral surface 7a formed in a cylindrical surface having a radius R, and arranged on both upper and lower sides with the main rotor chamber 7 interposed therebetween. The inner peripheral surfaces 8 a and 9 a of the upper and lower sub-rotor chambers 8 and 9 are formed as cylindrical surfaces having a radius r smaller than the inner peripheral surface 7 a of the main rotor chamber 7.

  The radius of the large diameter portion 15a of the main rotor 15 having the main rotor side surface formed in a convex lens shape is set to be the same as the radius R of the cylindrical surface of the main rotor chamber 7, and the center of the main rotor 15 is the main rotor. The main rotor 15 is pivotally supported in the main rotor chamber 7 so as to coincide with the center 7 b of the chamber 7. Since the center 7b of the main rotor chamber 7 matches the center of the main rotor 15, the center of the main rotor 15 is also indicated as 7b.

  Further, the side surface shape of the sub-rotor is formed in a convex lens shape, and the radius of the large-diameter portions 16a, 17a of the lower sub-rotor 16, 17 is the same as the radius r of the cylindrical surfaces 8a, 9a of the upper and lower sub-rotor chambers 8, 9. With the center of the upper sub-rotor 16 aligned with the center 8b of the upper sub-rotor chamber 8, and the center of the lower sub-rotor 17 aligned with the center 9b of the lower sub-rotor chamber 9, the upper and lower sub-rotors 16, 17 The upper and lower sub-rotor chambers 8 and 9 are pivotally supported in a rotatable manner. Further, since the centers 8b and 9b of the sub-rotor chambers 8 and 9 and the centers of the sub-rotors 16 and 17 coincide with each other, the centers of the sub-rotors 16 and 17 are also displayed as 8b and 9b.

Distances L between the main rotor chamber center 7b and the centers 8b and 9b of the upper and lower sub-rotor chambers 8 and 9, the radii R and Ra of the large diameter portion 15a and the small diameter portion 15b of the main rotor 15, and the upper and lower sub rotors Between the radii r and ra of the 17 large diameter portions 16a and 17a and the small diameter portions 16b and 17b,
L ² = R ² + r ² (1)
L = R + ra = Ra + r (2)
R, Ra, r, ra, and L are set so that the following relational expression holds.

  As shown in FIG. 1, in order to form the upper half portion of the main rotor 15, the main rotor chamber is formed on a straight line connecting the sub-rotor chamber center 8b of the upper sub-rotor chamber 8 and the sub-rotor chamber center 9b of the lower sub-rotor chamber 9. A circle having a radius L = (Ra + r) is centered on a rotor circumferential surface center 15d that is separated from the center 7b by a distance corresponding to the radius r of the large-diameter portion 16a of the sub-rotor 16 from the center 7b toward the sub-rotor chamber center 9b. The outer peripheral surface 15c of the main rotor 15 can be obtained by drawing up to the location intersecting the inner peripheral surface 7a and drawing the lower half of the main rotor 15 in the same manner as described above.

  As shown in FIG. 2, in order to form the lower half of the upper sub-rotor 16, the sub-rotor is formed on a straight line connecting the main rotor chamber center 7b of the main rotor chamber 7 and the sub-rotor chamber center 8b of the upper sub-rotor chamber 8. A circle having a radius L = R + ra is centered on a rotor peripheral surface center 16d that is separated from the chamber center 8b by a distance corresponding to the radius R of the large-diameter portion 15a of the main rotor 15 in a direction away from the main rotor chamber center 7b. By drawing up to the point where it intersects the inner peripheral surface 8a of the upper sub-rotor chamber 8 and turning it upside down, the outer peripheral surface 16c of the upper sub-rotor 16 can be obtained. Also, the outer peripheral surface 17c of the lower sub-rotor 17 can be obtained by performing the same operation.

  As described above, FIG. 1 illustrates a state in which the large-diameter portions 16a and 17a of the upper and lower sub-rotors 16 and 17 are in contact with the small-diameter portion 15b of the main rotor 15, and the small-diameter portions 16b of the upper and lower sub-rotors 16 and 17, respectively. 17b, the state in which the large-diameter portion 15a of the main rotor 15 is in contact with each other also in the state shown in FIG. 3 other than the state shown in FIG. The main rotor 15 and the upper and lower sub-rotors 16 and 17 can rotate while the large-diameter portions 16a and 17a are always in contact with each other, or the large-diameter portion 15a of the main rotor 15 is in the upper and lower sub-rotors 16 and 17, respectively. The fact that the main rotor 15, the upper sub-rotor 16, and the lower sub-rotor 17 can rotate while always in contact with the outer peripheral surfaces 16c and 17c will be described.

From the state illustrated in FIG. 1, as illustrated in FIG. 3, the rotor circumferential surface center 15 d when the main rotor chamber center 7 b of the main rotor chamber 7 is the origin and the main rotor 15 is rotated clockwise by an angle α. The positions in the X and Y directions are
X direction -rsinα
Y direction -rcosα
It is.

The X direction and Y direction positions of a point 15e passing through the main rotor peripheral surface center 15d and intersecting the upper outer peripheral surface 15c of the main rotor 15 with a line parallel to the Y axis are:
X direction -rsinα (4)
Y direction R + ra-rcosα (5)
It is.

Further, from the state illustrated in FIG. 1, as illustrated in FIG. 3, the X-direction and Y-direction positions of the large-diameter portion 16 a of the lower portion of the upper sub-rotor 16 are
X direction -rsinα (6)
Y direction L-rcosα = R + ra-rcosα (7)
Since the above equations (4) and (6) are equal and the above equations (5) and (7) are equal, the large-diameter portion 16a of the upper sub-rotor 16 is always in contact with the outer peripheral surface 15c of the main rotor 15. As a result of the rotation of the main rotor 15 and the upper sub-rotor 16, one main rotor chamber space 7c and the other main rotor chamber space 7d in the main rotor chamber 7 partitioned by the main rotor 15 and the upper sub-rotor 16 are mutually connected. It is possible to reliably maintain a sealed state without communicating with.

  Further, as shown in FIGS. 4 to 6, in the equation (2), an inter-axis distance L between the main rotor 15 and the upper and lower sub-rotors 16 and 17 is set, and the large-diameter portion 15a of the main rotor 15 is If one of the radius R or the radius r of the large diameter portions 16a, 17a of the upper and lower sub-rotors 16, 17 is set, the volume of the main rotor chamber 7 and the upper, lower sub-rotor chamber 8, The compression ratio of the rotor housing 1 can be selected by appropriately changing the volume of 9.

In the boundary point P ₁ between the main rotor chamber 7 and the upper Saburota chamber 8 and the lower Saburota chamber 9, as illustrated in FIG. 4, a large diameter portion 15a of the main rotor 15, a large diameter portion 16a of the upper Saburota 16 There contact with each other, the distance R ₁ between the main rotor chamber center 7b and boundary point P ₁ of the main rotor chamber 7, the distance r ₁ between Saburota chamber center 8b and boundary point P ₁ of the upper Saburota chamber 8, the main The distance L between the rotation center 7b of the rotor chamber 7 and the rotation center 8b of the upper sub-rotor chamber 8 is:
Formula (1) L ² = R ₁ ² + r ₁ ²
Since conditions are satisfied, the included angle of the main rotor chamber center 7b, and the line segment between the boundary points P _1, Saburota chamber center 8b, the line segment between the boundary point P ₁ is a right angle at the Pythagorean theorem.

5 and 6, when the radius of the large diameter portion 15a of the main rotor 15 is set to R ₂ and R ₃ , the radius r of the large diameter portion 16a of the upper sub-rotor 16 is set. ₂ and r ₃ are inevitably determined by the above equation (2), and the boundary points P ₂ and P ₃ exist on the semicircle Q whose diameter is the line segment L. As a result, FIGS. The illustrated rotary internal combustion engine 0 is also adapted to the present invention, and the ratio of the maximum volume of the main rotor chamber 7 and the maximum volume of the upper sub-rotor chamber 8 of these rotary internal combustion engines 0 can be changed as appropriate. A compression ratio is obtained.

  Hereinafter, the first embodiment shown in FIGS. 7 to 20 will be described.

  As shown in FIG. 10, the rotor housing 1 constituting the outer shell of the rotary internal combustion engine 0 is formed in a shape in which a semicircle having a smaller diameter is integrally attached to both upper and lower outer sides of a large diameter circle. The front and rear side panels 2 and 3 and the round shell 4 formed on the peripheral wall 2a and 3a of the side panel 2 and 3 along the outer peripheral edges 2a and 3a are formed. A bolt insertion hole 4b is formed in the vicinity of the cross-thickness portion 4a between the large-diameter circle and the small-diameter circle in FIG. 4, and the round shell 4 crosses the outer peripheral edge portions 2a and 3a of the pair of front and rear side panels 2 and 3 Bolt insertions 2b and 3b are respectively formed at locations corresponding to the thick portions 4a, bolts 5 are inserted into the bolt insertion holes 2b, 4b and 3b, and nuts 6 are inserted into the male threads 5a at the tips of the bolts 5. Screw By being tightened, the rotor housing 1 having a sealed therein 7, 8 and 9 is adapted to be configured.

  Further, the drive shaft 10 is rotatably supported through a main rotor shaft through hole 2c of the front side panel 2 via a bearing (not shown), and via a bearing (not shown). A drive shaft 10 is rotatably supported through the drive shaft through hole 3c of the rear side panel 3.

  The drive shaft 10 passes through the center of a main rotor 15 formed in a convex lens shape when viewed from the front of the vehicle body and is integrally coupled to the main rotor 15. The main rotor chamber 7 is connected to the main rotor 15 by the main rotor 15. It is divided into a chamber space 7c and the other main rotor chamber space 7d.

Further, the sub-rotor shaft of the rear side panel 3 is pivotally supported by the sub-rotor shaft pivot hole 2d of the front side panel 2 via a bearing (not shown) and via a bearing (not shown). The sub-rotating shaft 11 is pivotally supported through the pivotal support hole 3d.
Further, it is pivotally supported by the sub-rotor shaft pivot hole 3c of the front side panel 3 via a bearing (not shown), and the drive shaft through hole of the rear side panel 3 via a bearing (not shown). The sub rotary shaft 12 is pivotally supported so as to pass through 3c. The sub-rotating shafts 11 and 12 pass through the centers of the sub-rotors 16 and 17 formed in a convex lens shape when viewed from the front of the vehicle body and are integrally coupled to the sub-rotors 16 and 17, respectively. , 17 is divided into one sub-rotor chamber space 8a, 9a and the other sub-rotor chamber space 8b, 9b.

Furthermore, a transmission gear pivot support hole 2e is formed in the front side panel 2 at the center between the center of the main rotor shaft through hole 2c and the sub rotor shaft pivot support hole 2d with the main rotor shaft through hole 2c interposed therebetween. The transmission gear pivot shaft 13 is integrally fitted in the transmission gear pivot hole 2e, and three pieces of the same size and the same shape are provided at the rear ends of the drive shaft 10, the sub-rotor rotation shaft 11 and the sub-rotor rotation shaft 12, respectively. The transmission gears 14 are integrally fitted, and the transmission gear pivot shaft 13 has the same dimensions as the three transmission gears 14 fitted to the drive shaft 10, the sub-rotor rotating shaft 11, and the sub-rotor rotating shaft 12. In addition, two transmission gears 14 having the same shape are rotatably attached. When the main rotor 15 rotates, the upper and lower pair of upper sub-rotor 16 and lower sub-rotor 17 are also the same as the rotation of the main rotor 15 via the transmission gear 14. Direction and same rotation It is adapted to be rotated in degrees.

  An intake port 18 and an exhaust port 19 are formed at the lower left and right ends of the round shell 4 adjacent to the left and right ends of the lower lower sub-rotor chamber 9 and open to the lower inner peripheral surface 7a of the main rotor chamber 7, respectively. 18 is connected to an intake pipe 20 provided on the rear rear side panel 3, and an exhaust port 19 is connected to an intake pipe 21 provided on the front front side panel 2. The upstream end of the intake pipe 20 is illustrated. In addition to being connected to an air cleaner, the downstream end of the intake pipe 21 is connected to a silencer (not shown).

  A fuel injection valve 22 is disposed on the left side of the upper sub-rotor chamber 8, and a spark plug 23 is disposed on the right side of the upper sub-rotor chamber 8.

  Since the first embodiment shown in FIGS. 7 to 20 is configured as described above, when the drive shaft 10 is driven to rotate in the direction of the arrow shown by a starter motor (not shown), it is filtered by an air cleaner (not shown). As shown in FIGS. 11 to 12, the sucked intake air is sucked into one main rotor chamber space 7 c of the main rotor chamber 7 from the intake pipe 20 through the intake port 18 and then one of the upper sub-rotor chambers 8. The sub-rotor chamber space 8c begins to be press-fitted.

  Then, the main rotor 15, the upper sub-rotor 16, and the lower sub-rotor 17 are further rotated clockwise from the state shown in FIG. 13 in which the large-diameter portion 16a of the upper sub-rotor 16 is in contact with the small-diameter portion 15b of the main rotor 15. As shown in FIG. 16, fuel is injected from the fuel injection valve 22 into the upper sub-rotor chamber 8c, and the intake air compression proceeds during the time shown in FIGS. 14 to 15, and before the time shown in FIG. Fuel injection stops.

  Further, the main rotor 15, upper and lower sub-rotors 16, 17 rotate clockwise from the state shown in FIG. 16, and the main rotor 15, upper and lower sub-rotors 16, 17 rotate from the state shown in FIG. Then, a part of the air-fuel mixture in the upper sub-rotor chamber space 8c flows into one main rotor chamber space 7c, and the air-fuel mixture in the upper sub-rotor chamber space 8c and the main rotor chamber space 7c is ignited by ignition of the spark plug 23. As the pressure of the combustion gas increases, the main rotor 15 is driven to rotate clockwise as shown in FIGS.

  When the main rotor 15 and the upper and lower sub-rotors 16 and 17 reach the position shown in FIG. 19 and exceed the position shown in FIG. 18, the fuel gas in the main rotor chamber space 7c is discharged from the exhaust port 19 to the exhaust pipe. When the main rotor 15 and the upper and lower sub-rotors 16 and 17 are further rotated from the state shown in FIG. 20, the state is returned to the state shown in FIG.

  The operation of the rotary internal combustion engine 0 described above is simultaneously performed with a half rotation difference between the left half portion and the right half portion of the rotary internal combustion engine 0. Therefore, the output per rotation is 2 of a normal 2-stroke cycle internal combustion engine. The value is four times that of a four-stroke cycle internal combustion engine.

  In the rotary internal combustion engine 0, the rotor housing 1, the main rotor 15, the upper sub-rotor 16, and the lower sub-rotor 17 have simple shapes and are not complicated in structure, so that the productivity is high and the cost is low.

  Next, the second embodiment shown in FIGS. 21 to 30 will be described.

  In the second embodiment, parts that are the same as in the first embodiment are given the same reference numerals.

  In the first embodiment, the intake port 18 and the exhaust port 19 are opened on the inner peripheral surface 7a facing the left space 7c and the inner peripheral surface 7a facing the right space 7d of the main rotor chamber 7, respectively. In the second embodiment, as shown in FIGS. 21 and 22, an intake port 24 communicating with the other sub-rotor chamber space 9 d corresponding to the left side of the lower sub-rotor chamber 9 is formed in the rear side panel 3. In addition, an exhaust port 25 communicating with one of the sub-rotor chamber spaces 9c corresponding to the right side of the lower sub-rotor chamber 9 is formed in the front side panel 2, and an intake pipe 20 and an exhaust pipe 21 are connected to the intake port 24 and the exhaust port 25, respectively. The intake port 24 and the exhaust port 25 are formed in a sector shape with a narrow angle close to a right angle as shown in FIG. 21, and the intake port 24 is in a range indicating 6 o'clock and 9 o'clock of the clock hand. Opening The exhaust port 25 is an opening in a range indicating 12 o'clock and 3 o'clock of the clock hand.

  Further, the transmission gear 14, which interconnects the drive shaft 10, the sub-rotor rotating shaft 11, and the sub-rotor rotating shaft 12, is omitted, but the mechanism that interconnects the driving shaft 10, the sub-rotor rotating shaft 11, and the sub-rotor rotating shaft 12 is omitted. In this case, instead of using the transmission gear 14, another communication mechanism may be used.

  Further, as shown in FIGS. 22 to 27, the rear surface of the front side panel 2 and the front surface of the rear side panel 3 are circular with the same diameter r as the inner peripheral surface 9 a of the lower sub-rotor chamber 9 of the round shell 4. Recesses 2f and 3f (3f not shown) are formed, and a front shielding disk 26 and a rear shielding disk 27 are integrally mounted on the front and rear end surfaces of the lower sub-rotor 17, and the front shielding disk 26 and the rear The shielding disk 27 has a substantially arc shape extending along the outer peripheral surface 17c of the lower sub-rotor 17 and extending in a direction perpendicular to the surface connecting the small-diameter portion 17b and the large-diameter portion 17a of the lower sub-rotor 17. Openings 26a and 27a are formed.

  Since the embodiment shown in FIGS. 21 to 30 is configured as described above, when the drive shaft 10 is driven to rotate from the rear to the front by a starter motor (not shown), an air cleaner (not shown) is used. As shown in FIGS. 22 to 24, the filtered intake air is drawn from the intake pipe 20 into the other sub-rotor chamber space 9d located on the left side through the intake port 24 and the opening 27a of the rear shielding disk 27. Further, the air is sucked into the other main rotor chamber space 7d of the main rotor chamber 7, and after the state shown in FIG. 24, fuel is injected from the fuel injection valve 22 into the one sub-rotor chamber space 8c.

  After the end of the compression stroke shown in FIG. 24 where the large diameter portion 15a of the main rotor 15 and the large diameter portion 16a of the upper sub-rotor 16 are in contact with each other, when the state shown in FIG. The air-fuel mixture in the space 8c is rotated clockwise in response to the rotation of the upper sub-rotor 16, and when the state exceeds the state shown in FIG. 26 and becomes the state shown in FIG. 27, the air-fuel mixture in one sub-rotor chamber space 8c. The air flows into the other main rotor chamber space 7c of the main rotor chamber 7, the spark plug 23 operates, the air-fuel mixture in one sub-rotor chamber space 8c is ignited and burned, and the pressure of this high-pressure combustion gas As a result, the main rotor 15 is rotated clockwise.

When the main rotor 15 and the upper and lower sub-rotors 16 and 17 are further rotated clockwise from the state shown in FIG. 27 to the state shown in FIG. 28, the combustion gas front shielding in the right main rotor chamber 7c is performed. When the exhaust gas passes through the exhaust pipe 21 through the opening 26a of the disk 26 and reaches the state shown in FIG. 29, the exhaust of the combustion gas is finished.
The rotary internal combustion engine 0 returns to the state intake state shown in FIG. 22 after the main rotor 15 and the upper and lower sub-rotors 16, 17 are further rotated clockwise from the state shown in FIG. The operation is repeated.

  In the embodiment shown in FIGS. 21 to 30 without FIG. 7, as in the embodiment shown in FIG. 20, the main rotor chamber 7, the upper sub-rotor chamber 8, and the lower sub-rotor chamber 9 are rotated during one rotation of the main rotor 15. In the space divided into two, the strokes of suction, compression, combustion, and exhaust are executed, respectively, so that the output per rotation is doubled or quadrupled compared to the conventional reciprocating internal combustion engine, The rotary internal combustion engine 0 can be downsized.

  Further, in the rotary internal combustion engine 0, since there is no reciprocating portion, there is little vibration and noise due to vibration can be avoided.

  In the first embodiment and the second embodiment, a water injection valve (not shown) can be provided on the downstream side of the spark plug 23. With such a structure, the in-cylinder cooling performance by vaporization latent heat and the fuel consumption by the vapor pressure are improved. In this case, the injection steam discharged from the water injection valve is blocked by the upper sub-rotor 16 and the spark plug 23 is prevented from getting wet, and the efficiency of the rotary internal combustion engine 0 can be improved. The degree of freedom in water injection timing and the location of the spark plug 23 is improved.

DESCRIPTION OF SYMBOLS 0 ... Rotary internal combustion engine, 1 ... Rotor housing, 2 ... Front side panel, 3 ... Back side panel, 4 ... Round shell, 5 ... Bolt, 6 ... Nut, 7 ... Main rotor chamber, 8 ... Upper subrotor chamber, 9 ... Lower sub-rotor chamber, 10 ... drive shaft, 11 ... sub-rotor rotation shaft, 12 ... sub-rotor rotation shaft, 13 ... transmission gear pivot shaft, 14 ... transmission gear, 15 ... main rotor, 16 ... upper sub-rotor, 17 ... lower sub-rotor, 18 ... intake port, 19 ... exhaust port,
20 ... Intake pipe, 21 ... Exhaust pipe, 22 ... Fuel injection valve, 23 ... Spark plug, 24 ... Intake port, 25 ... Exhaust port, 26 ... Front shielding disk, 27 ... Back shielding disk

Claims (6)

One main rotor chamber (7) having an inner peripheral surface formed in a cylindrical surface (7a), and disposed on both sides of the main rotor chamber (7), and an inner peripheral surface is the main rotor chamber (7 A rotor housing (1) formed with two sub-rotor chambers (8, 9) formed on a cylindrical surface (8a, 9a) having a smaller diameter than the cylindrical surface (7a) of
A main rotor (15) having a convex lens-like shape on the side surface of the main rotor rotatably supported in the rotor housing (1) in close contact with the inner peripheral surface (7a) of the main rotor chamber (7);
A sub-rotor (16, 17) having a convex lens-like shape on the side surface of the sub-rotor pivotally supported by the rotor housing (1) in close contact with the inner peripheral surfaces of the two sub-rotor chambers (8, 9);
An intake port that communicates with one of the two sub-rotor chambers (8, 9) or a part of one main rotor chamber (7) adjacent to the one sub-rotor chamber (9). (18, 24),
An exhaust port (19) communicating with one subrotor chamber (9) of the two subrotors (8, 9) or a part of the other main rotor chamber (7) adjacent to the one subrotor chamber (9). , 25) and
A combustion chamber (8d) formed in the other sub-rotor chamber (8) of the two sub-rotor chambers (8, 9);
The one main rotor (15) and the two sub-rotors (16, 17) are connected together so as to be rotatable in the same direction and at the same rotational speed, and the rotation shaft (10) of the main rotor (15). A rotary internal combustion engine (0) comprising a power transmission mechanism (14) for taking out power from the engine. The diameter of the circumferential surface (7a) of the main rotor chamber (7) and the large diameter of the main rotor (15) are R,
The diameter of the circumferential surface (8a, 9a) of the sub-rotor chamber (8, 9) and the large diameter of the sub-rotor (16, 17) are r,
The main rotor (15) and the sub rotors (16, 17) have small diameters Ra, ra,
When the distance between the rotation center (7b) of the main rotor (15) and the rotation center (8b, 9b) of the sub-rotor (16, 17) is L,
L ² = R ² + r ² (1)
R + ra = Ra + r (2)
The rotary internal combustion engine (0) according to claim 1, wherein the following relational expression is established. The main rotor (15) is located away from the center (7b) of the main rotor (15) toward the small diameter portion (15b) by a distance corresponding to the large diameter (r) of the sub rotor (16, 17) (15d )
Formed in a shape along the cylindrical surface (15c) of radius L,
The sub-rotor (16, 17) is directed from the center (8b, 9b) of the sub-rotor (16, 17) to the small diameter portion (16b, 17b),
A location separated by a distance corresponding to the large diameter (R) of the main rotor (15) is the center (16d),
The rotary internal combustion engine (0) according to claim 2, wherein the rotary internal combustion engine (0) is formed in a shape along a cylindrical surface (16c, 17c) having a radius L.   The opening of the intake port (18) and the opening of the exhaust port (19) are respectively formed on the peripheral wall (7e) of the main rotor chamber (8) adjacent to the sub-rotor chamber (9) on the intake / exhaust side. The rotary internal combustion engine (0) according to any one of claims 1 to 3, wherein the rotary internal combustion engine (0) is characterized.   The opening (25a) of the exhaust port (25) is formed on the side wall of the main rotor chamber adjacent to one sub-rotor chamber where the intake / exhaust port is disposed, and the opening (24a) of the intake port (24) The rotary internal combustion engine (0) according to any one of claims 1 to 3, characterized in that is formed on a side wall (2) on a side surface of the one sub-rotor chamber (9).   Water injection to the downstream side of the sub-rotor (16) in the other sub-rotor chamber (8) with respect to the spark plug (23) provided in the other sub-rotor chamber (8) in which the combustion chamber (8d) is formed. The rotary internal combustion engine (0) according to any one of claims 1 to 5, further comprising a water injection valve for performing the following operation.

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