JPS6345482B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION According to the present invention, a crankshaft is rotatably mounted in eccentric holes of rotary bearings rotatably mounted on both sides of an engine, and a polygonal piston is mounted on the eccentric portion of the crankshaft. The rotary bearing is rotatably mounted, and as the crankshaft rotates, the rotating bearing rotates in the opposite direction to the crankshaft, and the center of the piston, which is mounted on the eccentric part of the crankshaft, moves along an approximate elliptical trajectory. , is a rotary piston engine in which the piston rotates and each vertex of the piston constantly slides along the inner surface of the body.

The basic principle of this engine is the patent application filed in 1978.
It is already known from No. 102845.

However, in the structure according to Patent Application No. 102845 of 1978, a rotary bearing that makes the locus of the center of the piston approximately elliptical is installed inside the piston, so the diameter of the crankshaft is controlled and the engine The disadvantage was that the strength was insufficient.

The present invention solves the above-mentioned drawbacks.
To explain the principle of the present invention with reference to the drawings, the first
2 in the figure is the inner surface of the body, and 11 is the rear rotating bearing of the rotary bearings rotatably mounted on both sides of the engine (in the detailed description of the invention, for convenience of explanation, the vertical cross-sectional view of FIG. The right side is the front of the engine and the left side is the rear of the engine), 14 is a crankshaft rotatably mounted in an eccentric hole in the rear rotation bearing, 1
5 is the eccentric part of the crankshaft, 17 is the piston, M is the center of the eccentric hole of the crankshaft and rear rotation bearing, N is the eccentric part of the crankshaft and the center of the piston, A is the piston rotatably mounted on the crankshaft. B is the pitch circle of the external gear 16 for positioning, and B is the pitch circle of the internal gear 18 fixed to the piston.

Further, in Fig. 5 (for the position of each gear, refer to the vertical cross-sectional view Fig. 6), F indicates the pitch circle of the external gear 20 fixed to the crankshaft, and G and H indicate the pitch circle of the gear 21 which extracts the rotation of the crankshaft. I is the pitch circle of the internal gear portion 22 and the external gear portion 23, I is the pitch circle of the external gears 25b and 25C fixed to the output shaft 24, and J is the pitch circle of the external gear 26C that transmits the rotation of the output shaft 24 to the rear rotation bearing 11. The circle K is the pitch circle of the external gear portion 12 of the rear rotation bearing 11.

The gears with pitch circles F, G, H, I, J, and K are combined so that when the crankshaft 14 rotates once clockwise, the rear rotation bearing 11 rotates once in the opposite direction, and the gears are mounted on the crankshaft. A piston positioning external gear 16 and an internal gear 18 fixed to the piston 17 are meshed to keep the rotation of the piston at one-third of the rotation of the crankshaft.

When the crankshaft 14 rotates clockwise from the position shown in FIG. The rear rotation bearing 11 rotates in the opposite direction of the rotation of the crankshaft.

Therefore, as shown in Figures 1 to 4 of the drawings,
The center M of the crankshaft 14 rotatably mounted in the eccentric hole of the rear rotation bearing 11 moves along the locus of a circle X, and the eccentric portion 15 of the crankshaft and the center N of the piston 17 form an approximate ellipse Y
The piston moves in the direction of rotation of the crankshaft at a rate of one-third of that of the crankshaft, and each vertex P, Q, R of the piston slides along the inner surface 2 of the body.

6, 7, 8, and 9 show a first embodiment of the present invention.

The structure is such that a rear rotation bearing 11 is rotatably mounted inside a bearing portion 8 of a rear support plate 7, and a crankshaft 14 with an external gear 20 fixed to an eccentric hole of the rear rotation bearing 11 is rotatably mounted. A gear 21 for taking out the rotation of a crankshaft 14 is rotatably mounted on the outside of a bearing part 8 of a rear support plate 7, and an internal gear part 22 of the gear 21 is meshed with an external gear 20.

An output shaft 24 rotatably mounted on the rear support plate 7
External gears 25b and 25C are fixed to
b is meshed with the external gear part 23 of the gear 21, and an external gear 26C that transmits the rotation of the output shaft 24 to the rear rotation bearing 11 is rotatably mounted on the outside of the rear support plate 7, and the external gear 26C is connected to the external gear 25C. and meshes with the external gear portion 12 of the rear rotation bearing 11.

The rear cover 35 and the rear side plate 4 of the body are attached to the rear support plate 7.

The airtight piece 37 and the side airtight piece 38 are attached, and the piston 17 to which the internal gear 18 is fixed is rotatably attached to the eccentric part 15 of the crankshaft, the body 1 is attached to the rear side plate 4 of the body, and the body 1 is attached to the body 1. Attach the front side plate 3.

A positioning external gear 16 of the piston rotatably passed through an eccentric hole of the front rotation bearing 9 is rotatably mounted on the crankshaft 14 and meshed with an internal gear 18 fixed to the piston.

An external gear 25a is fixed to the output shaft 24, and an external gear 26a is rotatably mounted on the front plate 3 of the body to transmit the rotation of the output shaft 24 to the front rotation bearing 9. It meshes with the external gear part 10 of the bearing.

A slider 30 is fixed to an external gear 16 for positioning the piston, a vertical slider 31 is slidably attached to the side surface of the slider 30, and an inner surface 6 on which the vertical slider 31 can slide up and down is provided. A support plate 5 is attached to the front side plate 3 of the body, and a front cover 34 is attached to the front support plate of the body. Note that 2 is the inner surface of the body, 19 is the inner surface of the piston, 40 is an intake port, 41 is an exhaust port, 43 is a sub-combustion chamber, 44 is a fuel injection nozzle, and 45, 46, and 47 are voids.

The positioning external gear 16 of the piston, which is rotatably mounted on the crankshaft 14, moves together with the crankshaft 14 when the crankshaft rotates clockwise and the front rotation bearing 9 rotates in the opposite direction. The internal gear 18 fixed to the piston is prevented from rotating by the inner surface 6 of the front support plate via the slider 30 fixed to the external gear 16 and the vertical slider 31.
By setting the gear ratio of the external gear 16 to 3:2, the piston 17 is aligned with the crankshaft 3 in the direction of rotation of the crankshaft 14.
The piston rotates at a rate of one rotation per rotation.
Figures 10, 11 and 12 show a second embodiment of the invention.

In the second embodiment, instead of the slider 30 fixed to the external positioning gear 16 of the piston in the first embodiment, an external gear 32 is fixed to the external positioning gear 16 of the piston, and an internal gear 32 is fixed to the external positioning gear 16 of the piston. A gear 33 is fixed, and an external gear 32 and an internal gear 33 are meshed.

With the structure of the second embodiment, the crankshaft 14 rotates clockwise, and the front and rear rotation bearings 9
and 11 rotate in the opposite direction, the external gear 32 fixed to the positioning external gear 16 of the piston moves against the front support plate 5 as the crankshaft 14 moves.
The piston positioning external gear 16, which meshes with the internal gear 33 fixed to the crankshaft 1 and rotates clockwise, and has the external gear 32 fixed thereto, rotates clockwise.
4, that is, in the same direction as the piston 17, the ratio of the number of teeth between the internal gear 18 fixed to the piston and the positioning external gear 16 of the piston is:
It can be made smaller than 3:2.

Therefore, compared to the engine of the first embodiment, the engine of the second embodiment has the advantage that the diameter of the crankshaft 14 can be made larger and the strength of the engine can be increased.

FIG. 13 shows a third embodiment of the present invention.

In the structure of the third embodiment, instead of the crankshaft 14 in the first embodiment, a shaft 51 is fixed to the front rotation bearing 9 and the rear rotation bearing 11.
A cylinder 52 having an eccentric portion 53 that performs an action corresponding to the crankshaft in the embodiment is rotatably mounted, an external gear 20 is fixed to the cylinder 52, and the front rotation bearing 9 is a bearing fixed to the front support plate 6. 54, the external gear 3 is rotatably mounted and fixed to the piston positioning external gear 16 in the second embodiment.
2 meshes with an internal gear 55 fixed to the front plate 3 of the body.

In addition, in the structure of the third embodiment, the front rotation bearing 9
can be used as an output shaft, and can also be used as an output shaft.
1, the output shaft 24 in the first embodiment transfers the rotation of the cylinder 52, which performs the function equivalent to the crankshaft 14 in the third embodiment, to the rear rotation bearing 11. ,
It is assumed that the shaft 56 is replaced with another gear.

The engine of the third embodiment has the advantage that the entire engine can be made smaller than the engines of the first and second embodiments.

The operating state of the rotary piston engine of the present invention will be explained with reference to the drawings. When the crankshaft 14 rotates clockwise from the position of the piston 17 as shown in figure 1 of FIG. 14, the gears 20, 21, 25b,
25a, 25C, 26a, 26C, 10 and 12
, the front rotation bearing 9 and the rear rotation bearing 11 rotate in opposite directions, and the piston 17 regards the positioning external gear 16 of the piston as a sun gear, and the internal gear 18 fixed to the piston as an internal planetary gear. Considering,
Rotate clockwise and move as shown in figure 2.
Figure No. 3 shows the crankshaft 14 turned one-half turn.

Next, the piston 17 passes through the state shown in figure 4 and returns to the state shown in figure 1.

Further, the output shaft 24 takes out the rotation of the crankshaft via an external gear 25b fixed to the output shaft, and rotates in the opposite direction of the crankshaft.

By repeating the above operations, the crankshaft rotates and the piston rotates.

Note that the gaps 45, 46, and 47 independently
Performs each stroke of suction, compression, expansion, and exhaust.

The object of the invention is to improve the Wankel engine. In the following description, the piston positioning external gear 16 will be referred to as the external gear 16.

The Wankel engine is as shown in Figure 15 of the drawing.
The eccentric part 15 of the crankshaft supports a piston 17 whose vertices are each apex of an equilateral triangle, the crankshaft 14 supports an external gear 16, and the internal gear 1
8 is attached to the piston 17, the internal gear 18 and the external gear 16 are meshed, and the ratio of the number of teeth between the internal gear 18 and the external gear 16 is 3:2.

In the Wankel engine, when the crankshaft 14 makes one rotation, the piston 17 revolves around the external gear 16 one rotation in the same direction as the crankshaft, and the piston 17 rotates one-third of a rotation in the same direction as the crankshaft.

The inner surface 2 of the body of the Wankel engine is created by the locus followed by each vertex of the piston as the crankshaft rotates, that is, by the epitrochoid curve of the following equation.

x=s・sinr+t・sin(r/3) y=s・cosr+t・cos(r/3) s: Distance between the centers of the eccentric portion 15 of the crankshaft and the crankshaft 14.

t: Distance from the center of the piston 17 to the top of the piston.

r: rotation angle of the crankshaft 14;

Note that M is the center of the crankshaft 14, and N is the center of the eccentric portion 15 of the crankshaft and the piston 17.

In the Wankel engine, the shape of the inner surface of the body, that is, the epitrochoid curve, is determined by the distance s and the distance t, and the design changes the shape of the gap at the end of compression, which is related to combustion efficiency when used as an internal combustion engine. The degree of freedom is low.

Means and operation for solving the problems of the Wankel engine of the present invention.

In order to change the epitrochoid curve, which is the locus followed by the apex PQR of the piston 17 of the Wankel engine, the present invention is as shown in FIG.
Rear rotation bearing 1 with a hole located eccentrically from the center
1 (In the present invention, a front rotation bearing 9 and a rear rotation bearing 11 are provided on both sides of the engine. These two parts support the crankshaft 14 on both sides of the engine. The functions of these parts produce exactly the same effect, so the explanation of the front rotation bearing 9 will be omitted.) is supported on the side of the engine, the crankshaft 14 is supported in the hole of the rear rotation bearing 11, and the When the rear rotation bearing 11 rotates once in the clockwise direction, the rear rotation bearing 11 rotates once in the counterclockwise direction, and the piston 1
Reference numeral 7 denotes an engine equipped with a mechanism that rotates one-third of a turn clockwise while revolving around an external gear 16 that makes one turn clockwise.

With this, the center M of the crankshaft 14
The trajectory followed by is given by the following formula.

x=u・sin(-r) y=u・cos(-r) Also, the center N of the eccentric part 15 of the crankshaft
The trajectory followed by is given by the following formula.

x=s.sinr+u.sin(-r) y=s.cosr+u.cos(-r) Therefore, the locus that each vertex of the piston follows due to the rotation of the crankshaft is expressed by the following equation.

x=s・sinr+u・sin(-r) +t・sin(r/3) y=s・cosr+u・cos(−r) +t・cos(r/3) u: From the center V of the rear rotation bearing to the rear rotation bearing The distance to the center M of the hole.

s: Distance from the center M of the hole in the rear rotation bearing to the center N of the eccentric part of the crankshaft.

t: Distance from the center N of the eccentric part of the crankshaft to the top of the piston 17.

r: Rotation angle of crankshaft.

The center of the crankshaft 14 is located at the same position as the center M of the hole in the rear rotation bearing, and the center of the piston 17 is located at the same position as the center N of the eccentric portion 15 of the crankshaft.

By changing the locus (epitrochoid curve) followed by the apex of the piston as the crankshaft rotates, the shape of the inner surface of the body changes, and the shape of the cavity upon completion of compression changes.

That is, by changing the length of the distance u (distance from the center V of the rear rotation bearing to the center M of the hole in the rear rotation bearing) without changing the ratio of the distance s and the distance t, the engine It is possible to change the compression ratio, making it possible to develop engines that require a high compression ratio.

In addition, in order to regulate the rotation of the rear rotation bearing 11 outside the body, Patent Application No. 102845 filed in 1972
The engine of Patent Application No. 102845 of 1972 does not require a mechanism inside the body to restrict the rotation of the rotary bearing that performs an action equivalent to the rear rotation bearing of the present invention inside the piston, which is required for the engine of Patent Application No. 102845 of 1972. In comparison, the engine of the present invention has increased strength inside the body.

Next, regulation of the rotation direction and rotation speed of the rear rotation bearing will be explained.

The rotation of the crankshaft 14 is caused by a gear group 20,
22, 23, 25b, 25c, 26c, and 12, and is transmitted to the rear rotation bearing 11.

When the crankshaft 14 rotates once clockwise, the external gear 20 rotates once clockwise.

The rotation direction and rotation speed of the internal gear portion 22 when the external gear 20 makes one rotation clockwise can be determined by calculation of the differential gear mechanism, but the ratio of the number of teeth between the external gear 20 and the internal gear portion 22 is For example, if the number of teeth of the external gear 20 = 21 and the number of teeth of the internal gear 22 = 24, the rotation direction of the internal gear 22 is the same as that of the external gear 20, and the rotation speed is three-quarters. It becomes rotation.

The rotation of the internal gear portion 22, that is, the rotation of the gear 21, is caused by the external gear portion 23 of the gear 21, the external gear 25b,
25c, 26c, external gear portion 1 of rear rotation bearing 11
2, and the rear rotation bearing 11 rotates.

Therefore, as an example: Number of teeth of external gear 20 = 21 teeth Number of teeth of internal gear portion 22 = 24 teeth Number of teeth of external gear portion 23 = 48 teeth Number of teeth of external gears 25b and 25c = 52 teeth of external gear 6c If the number of teeth is 30, and the number of teeth in the external gear portion 12 is three-quarters of the number of teeth in the external gear portion 23, or 36 teeth, the rear rotation bearing 11 rotates at the same number of rotations in the opposite direction as the crankshaft 14. do.

In addition, to explain the regulation of the rotation direction and rotation speed of the piston 17, in the first embodiment, since the rotation of the external gear 16 is prevented by the slider 30 and the vertical slider 31, the internal gear 18 is prevented from rotating. The rotation of the piston 17 is regulated by setting the tooth ratio of the external gear 16 to 3:2.

The rotation direction and rotation speed of the external gear 16 in the second embodiment are as follows:
2 and the internal gear 33 mounted on the front support plate 5 are determined by calculating the differential gear mechanism.
6 and the internal gear 18 by calculating the rotational direction and rotation speed of the internal gear 18, the gear group 1
8, 16, 32, and 33, and when the crankshaft 14 rotates once, the piston 1
7 revolves around the external gear 16 once in the same direction as the crankshaft, and rotates one-third of the way.

For example, if the number of teeth on the internal gear 18 = 36, the number of teeth on the external gear 16 = 26, the number of teeth on the external gear 32 = 39, and the number of teeth on the internal gear 33 = 42, then the crankshaft 14 is clocked. When the rear rotation bearing 11 makes one rotation in the direction, the rear rotation bearing 11 makes one rotation in the counterclockwise direction, so the external gear 32 rotates 3/39 in the clockwise direction. Multiplying the number of teeth of external gear 16 (26 teeth) by 36/39 gives 24 teeth,
As a result, the internal gear 18 revolves one revolution clockwise and one third revolution in the same way as the internal gear 18 with 36 teeth revolves around the non-rotating external gear 16 with 24 teeth. Rotate in the direction.

The engine of the present invention has the advantages of a simple structure, small size and light weight, and can perform extremely high compression, so it is effective as an engine, compressor, etc.

[Brief explanation of the drawing]

Figures 1, 2, 3, and 4 are diagrams of the principle of this invention, Figure 5 is a diagram of gear combinations for supplementary explanation of the principle of this invention, and Figure 6 is
7 is a sectional view of the piston portion of the first embodiment, FIG. 8 is a sectional view of the front support plate portion of the first embodiment, and FIG. 9 is a rear support of the first embodiment. A cross-sectional view of the plate portion, FIG. 10 is a longitudinal cross-sectional view of the second embodiment,
FIG. 11 is a sectional view of the piston part of the second embodiment;
FIG. 12 is a sectional view of the front support plate portion of the second embodiment;
FIG. 13 is a longitudinal sectional view of the third embodiment, FIG. 14 is an exploded view of the operation of each stroke, FIG. 15 is an explanatory diagram of the Wankel engine, and FIG. 16 is an explanatory diagram of the mechanism of the engine of the present invention. 1...Body, 2...Inner surface of the body, 3...
Front side plate of the body, 4... Rear side plate of the body, 5...
Front support plate, 6... Inner surface of front support plate, 7... Rear support plate, 8... Bearing portion of rear support plate, 9... Front rotation bearing, 10... External gear portion of front rotation bearing, 11 …
... Rear rotation bearing, 12 ... External gear part of rear rotation bearing, 14 ... Crankshaft, 15 ... Eccentric part of crankshaft, 16 ... Piston positioning external gear, 17 ... Piston, 18 ... Piston Internal gear fixed to 19...inner surface of piston,
20...External gear, 21...Gear for extracting the rotation of the crankshaft, 22...Internal gear portion of gear 21, 23...External gear portion of gear 21, 24...Output shaft, 25a, 25b, 25C... External gears fixed to the output shaft, 26a and 26C... External gears that transmit the rotation of the output shaft to the front and rear rotation bearings, 30...
Slider, 31... Vertical slider, 32...
...External gear, 33...Internal gear, 34...Front cover,
35...Rear cover, 37...Airtight piece, 38...Side airtight piece, 40...Intake port, 41...Exhaust port, 43
... Sub-combustion chamber, 44 ... Fuel injection nozzle, 45,
46, 47...Gap, 51...Axle in the third embodiment, 52, 53...The tube and the eccentric part of the tube in the third embodiment, respectively, 54...Bearing, 55...The body in the third embodiment Internal gear fixed to the front plate, 56... shaft, M... crankshaft 14,
The center of the hole in the front rotation bearing 9 and the hole in the rear rotation bearing 11, V...The center of the front rotation bearing 9 and the rear rotation bearing 11, N...The center of the eccentric part of the crankshaft and the piston, X...The center of the crankshaft Locus of the center, Y... Locus of the eccentric part of the crankshaft and the center of the piston, A... Pitch circle of the piston positioning external gear 16, B... Pitch circle of the internal gear 18 fixed to the piston, F... Pitch circle, G and H of the external gear 20...the internal gear portion 22 and the external gear portion 2 of the gear 21 that extracts the rotation of the crankshaft
3 pitch circle, I...Pitch circle of the external gears 25a, 25b, 25C fixed to the output shaft 24, J...Pitch circle of the external gears 26a and 26C that transmit the rotation of the output shaft 24 to the front and rear rotation bearings, K...10 and 12 pitch circles of the external gear portions of the front and rear rotation bearings, P, Q, R...each vertex of the piston 17.

Claims (1)

[Claims] 1. Plates are attached to both sides of the body 1, the front rotation bearing 9 and the rear rotation bearing 11 are supported by the plates attached to both sides of the body 1, and the piston positioning external gear 16 is connected to the crank. An eccentric portion 5 of a cylinder 52 supported by the shaft 14 or a shaft 51 and rotatably attached to the shaft 51
3 or the eccentric part 15 of the crankshaft supports a piston 17 whose vertices are each apex of an equilateral triangle, and meshes an internal gear 18 attached to the piston 17 with an external gear 16 for positioning the piston. A hole is provided in a position eccentric from the center, a hole is provided in a position eccentric from the center of the rear rotation bearing 11, and a hole in the front rotation bearing 9 and a hole in the rear rotation bearing 11,
The crankshaft 14 or the shaft 51 is supported, and the external gear 20 is attached to the crankshaft 14 or the cylinder 52.
The output shaft 24 or shaft 56 with the external gears 25b and 25c mounted thereon is rotatably mounted on the outside of the body 1, and the gear 21 is rotatably mounted on a plate mounted on the side surface of the body 1. , the external gear 20 is meshed with the internal gear portion 22 of the gear 21, the external gear 25b is meshed with the external gear portion 23 of the gear 21, and the external gear 26c is meshed with the plate attached to the side surface of the body 1.
is rotatably mounted, the external gear 25c is meshed with the external gear 26c, and the external gear 26 is attached to the external gear portion 12 of the rear rotation bearing 11.
C and slider 3 to the piston positioning external gear 16.
0 is attached, the vertical slider 31 is slidably attached to the slider 30, and the vertical slider 31 is slidably attached to the slider 30.
is slidably attached to a plate attached to the side surface of the body 1 to prevent rotation of the piston positioning external gear 16, or an external gear 32 is attached to the piston positioning external gear 16, and the external gear 32 is attached to the piston positioning external gear 16. An internal gear that meshes with the crankshaft 14 is attached to a plate attached to the side surface of the body 1 to regulate the rotation of the piston positioning external gear 16.
Alternatively, a rotary piston engine characterized in that the outline is created by a curve that each vertex P, Q, and R of the piston follows when the cylinder 52 rotates once.