JPS6229614B2 - - Google Patents

Description

[Detailed Description of the Invention] <Industrial Application Field> This invention relates to a rotary engine in which a rotor that has good sealing properties and can freely design a compression stroke and an expansion stroke slides on the inner surface of a casing. In particular, in order to cope with gas leakage caused by the vane being pushed away by compressed high-pressure gas, the tip of the vane is bent so that its curved outer peripheral surface is in sliding contact with the rotor housing, and the side surface of the vane is always A highly economical rotary engine that is provided with a groove communicating with a chamber on the low pressure side and that allows the vanes to expand and contract slightly on both sides, has a simple structure, is inexpensive to manufacture, and can be operated at low cost. This invention relates to.

<Prior art> As is well known, conventional vane type rotary engines have two configurations: one in which the vanes slide against the inner peripheral surface of the casing, and the other in which the vanes have a structure that controls movement with a certain clearance.The latter has a control structure. From the above constraints, the compression stroke and expansion stroke have the same volume.

The rotary engine that has now been successfully put into practical use is an engine that revolves around a rotor.

<Problems to be solved by the invention> The structure of the conventional rotary engine is
The disadvantage is that the design and processing of vanes, rotors, rotor shafts, rotor housings, etc. are extremely complicated.Furthermore, since the structure is complex and includes a valve mechanism and gear mechanism, it is easy to break down. It has disadvantages such as being easy to repair and troublesome to repair.

For example, the invention is disclosed in Japanese Patent Application Laid-Open No. 13009/1983. This is a problem common to rotary engines and the like, but the conventional invention had the disadvantage that distortion of the casing due to high pressure gas could not be realized by gas release by pushing back the vane or the like.

Further, the well-known rotary engine has the disadvantage that it is difficult to use multiple cylinders, and it is difficult to design and manufacture a high-output engine.

<Objective of the Invention> The object of the present invention is to solve the problems of the rotary engine based on the above-mentioned prior art, and to solve the above-mentioned drawbacks, overcome the difficulties, eliminate the disadvantages, design, and process. It is easy to design and manufacture a large-scale engine, and the structure is simple, there are few failures, and the operating cost is low and economical. The aim is to provide an excellent rotary engine that will benefit the field.

<Means/actions for solving the problems> In order to solve the above-mentioned problems, the structure of the present invention, which is based on the above-mentioned claims, is to replace the elliptical and flat rotor housing with a cylindrical shape. As the rotor rotates, the premixed gas of fuel and air is taken in from the intake port and is sequentially compressed in the chamber between each vane, which is housed in a set number of storage grooves in the circumferential direction formed radially on the rotor.
During this time, compressed gas enters the storage groove from the groove bored on the leading side of the vane, presses the vane tip from the bottom against the inner peripheral surface of the rotor housing, creating a gas seal, and also seals the vane against the inner peripheral surface of the rotor housing. In this case, the intrusion pressure by the phase notch applies lateral pressure to both sides, and the gas seal is created by the pressure difference between the gas pressure intruding into the groove formed on the side surface, and the frictional force of the vane is increased only by high pressure. The sliding resistance should not be large, and during the compression stroke, the burnt high-pressure gas from the combustion chamber flows back and irreversibly compresses the unburned premixed gas, and at the same time raises the temperature of the fuel premixed gas. By igniting and exploding, the rotor is rotated so that even an ultra-dilute premixture that is below the ignition limit in normal combustion can be ignited and burned, and the rotor is rotated by 180 degrees. The inner peripheral surface of the casing is formed so that the centers of gravity of two opposing vanes set at an angle of In addition, the work of exhaust gas is utilized to reach atmospheric pressure, so that fluctuations in exhaust pressure do not occur, and the suction and exhaust strokes are performed continuously to make suction and exhaust noise. In addition to significantly reducing the amount of gas, the combustion cycle combines the advantages of the Otto cycle and the Brate cycle, in which almost constant volume changes occur in the high-temperature heating section and low pressure changes occur in the low-temperature heat dissipation section. High thermal efficiency is realized, and at the same time near the top dead center of the compression stroke, burnt gas is injected back into unburnt gas, and the blown burnt gas is used for mixed ignition combustion to achieve an ultra-low air-fuel ratio. By forcing the mixture to burn
The exhaust harmful components such as NOx, CO, and H are significantly reduced, and electric ignition is provided.
This technology eliminates radio wave pollution, always recirculates exhaust gas at a constant volume ratio, and ensures stable combustion regardless of rotational speed.

<Embodiment - Configuration> Next, one embodiment of the present invention will be described below based on the drawings.

1 and 2 are embodiments showing a cross-sectional view and a vertical cross-sectional view of a half part of the rotary engine of the present invention,
The rotary engine has a straight rotor shaft 1, a substantially cylindrical rotor 2, and the rotor 2 is in sliding contact,
It has an oval rotor housing 3 and both side housings 6, 6.

A large number of vane accommodating grooves 4, 4, . The vane 5 is inserted so as to be movable in the radial direction with respect to the rotor axis, and extends to the bottom of the vane housing groove 4 on its leading edge side surface, that is, the surface facing the rotation direction. A narrow groove 5a is bored as shown in FIG.

The narrow groove 5a is attached to the bottom of the vane housing groove 4 in order to introduce high pressure gas, which will be described later, and each vane 5,
〓〓〓〓
5', and a chamber R partitioned by the outer circumferential surface of the rotor 2 and the inner circumferential surface 3' of the rotor housing 3.
are designed to effectively seal each other.

Therefore, each vane 5 has a shape as shown in FIGS. 3 and 4.
It can be divided into two piece parts 5A and 5B at the center in the longitudinal direction, and the opposing mating surfaces 5b of these two parts 5A and 5B have a Z-shape as shown in FIG. The so-called “sekiri” “phase cut”
The two "phase-notched" parts are connected by a "phase-notched joint" so that a slight relative movement in parallel to the axis of the rotor 2 is allowed.

In addition, grooves 5c are formed on both sides of each vane 5, that is, on the outer surfaces of each of the parts 5A and 5B forming pieces of each vane 5, as shown in FIGS. 2 and 5. It communicates with a small hole 5d opened in the tip surface of the vane 5.

The small hole 5d is for introducing the gas in the low pressure side chamber into the groove 5c, that is, it is for introducing low pressure premixed gas or low pressure combustion gas into the groove 5c regardless of the rotation angle of the vane 5. It is drilled in such a position that it can be obtained.

Therefore, although low-pressure mixed gas flows into the groove 5c from the small hole 5d at the tip of the vane 5 at the sliding contact surface between each vane 5 and the side housings 6, 6, the central part of the vane 5 "phase notch" 5b
Due to the pressure difference between the high-pressure gas entering the vane 5, the piece parts 5A and 5B of both halves of the vane 5 move as shown by the arrow A in FIG.
As shown in the figure, a lateral biasing force is applied as a result, and each vane 5 is pressed against both side surfaces, and gas sealing of both sides to the side housings 6, 6 is performed.

In this case, if only high pressure gas is used, the vane 5
The pressing force against the inner surface of the side housing 6 is prevented from increasing and the sliding resistance is prevented from increasing, and the rotation of the vane 5 is guaranteed by resistance while ensuring a smooth and sealed state.

In addition, in Fig. 4, P ₁ and P ₂ are piece portions 5
The direction and pressure distribution of the pressure on the opposing mating surfaces of a and 5b, that is, the recessed portion 5b,
P ₃ and P ₄ indicate the direction and pressure distribution of pressure on both left and right sides, and the resultant force of P ₁ and P ₂ is always larger than the resultant force of P ₃ and P ₄ . .

As can be seen from the figures, each vane 5 has its tip bent in the opposite direction to the rotating direction of the rotor 2. As shown, rotor housing 3
It is configured to be an arcuate surface with a large curvature that is different from the curvature of the inner peripheral surface.

Then, as shown in FIGS. 6 and 7, the vane 5
The curvature of the tip surface 5e of the vane 5 and the curvature of the inner circumferential surface 3' of the rotor housing ₃ are as follows _: It is determined that the rotor always slopes toward the high pressure side chamber regardless of the rotation angle of the rotor.

Therefore, as the rotation angle of the rotor 2 changes, the position of the tip surface 5e of the vane 5 that contacts the rotor housing inner circumferential surface 3' changes, but this is because the tip surface 5e of the vane 5 is bent. In combination with this, the sealing effect of each vane 5 is further enhanced, and a well-balanced structure in terms of strength design can be obtained.

To explain this in more detail, FIG. 6 shows the state of contact between the tip end surface 5e of the vane 5 and the inner circumferential surface 3' of the rotor housing 3 during the compression stroke.
The left side chamber 7R in the diagram of vane 5 is P ₅ more than the right side chamber 8R.
As shown, the pressure is low, and high pressure gas is introduced from the high pressure side chamber 8R into the vane housing groove 4 of the vane 5 through the groove 5a on the leading edge side surface of the vane 5.

Therefore, as a result, the vane 5 is potentially given a force that presses it against the inner circumferential surface 3' of the rotor housing 3 with strong pressure.

Also, in the low-pressure side chamber 7R, the tips of the vanes 5 are pushed upward by the low-pressure gas from below, and the upward pressure distribution _P5 is
This is shown on the lower side of the figure, and similarly, the vane 5 potentially has a force that presses against the inner circumferential surface 3' of the rotor housing 3.

On the other hand, the force pushing the vane 5 into the vane housing groove 4 is caused by the force of the low pressure and high pressure gas pushing down the vane tip and the reaction force from the inner peripheral surface 3' of the rotor housing 3. Yes, but Vane 5
The curvature of the tip surface 5e of the rotor housing 3 is different from the curvature of the inner peripheral surface of the rotor housing 3, and as mentioned above, the tangential line
Since L ₁ and L ₂ are inclined toward the high pressure side, the area facing the high pressure side of the tip surface 5e of the vane 5 in contact with the inner circumferential surface 3' of the rotor housing 3 is reduced.
As a result, the downward reaction force received from the inner circumferential surface 3' of the rotor housing 3 is considerably smaller than the force pushing up the vane 5, and as a result, the vane 5 is formed on the inner circumferential surface 3' of the rotor housing 3. It will be pressed with a sufficiently large force.

Note that the downward pressure distribution acting on the tip of the vane 5 is indicated by the symbol P ₆ on the upper left side of FIG. 6.

Next, in FIG. 7, a state in the expansion stroke is shown, and the high-pressure side chamber 9R is on the left side of the vane 5 in the figure, and the low-pressure side chamber 10 is on the right side of the vane 5.

Therefore, in this case, the gas introduced into the vane housing groove 4 is the low-pressure side chamber 10R, and the force pushing up the tip of the vane 5 is due to the gas in the high-pressure side chamber 9R. The pressure distribution of the force pushing up the vane 5 is as shown in P ₇ at the bottom left of the figure.

On the other hand, the downward force acting on the vane 5 is applied to the inner peripheral surface 3' of the rotor housing 3 at the tip of the vane 5.
This is a strong reaction force, which is the sum of the force pushing down the gas in the high pressure side chamber 9R and the force pushing down the leading edge side tip surface 5e of the vane 5 by the gas in the low pressure side chamber 10R, resulting in downward pressure. The distribution looks like P ₈ in the upper right of the figure.

Therefore, the sum of the forces becomes an upward force and Vane 5
is brought into pressure contact with the inner circumferential surface 3' of the rotor housing 3.

In this case, the position of the tip surface 5e of the vane 5 that contacts the inner peripheral surface 3' of the rotor housing 3 is on the trailing edge side of the vane 5, as shown in the figure, and the tangent line L ₂ at this position is is high pressure side chamber 9
This is because it will be inclined toward R.

As shown in FIG. 2, the rotor housing 3 is provided with an intake port 3A and an exhaust port 3B at approximately symmetrical positions, and a passage 3C that communicates with the combustion chamber 11 and the chamber 12 immediately in front of it is provided at the top. It is set in.

A glow plug 3D for igniting at the time of starting is arranged in the passage 3C, and gasoline is supplied from an appropriate carburetor attached to a portion before the intake port (not shown) and mixed with intake air to form a premixed gas. is being used.

The premixed gas is ignited by a glow plug at the time of startup, but once ignited during the operating process, the burnt gas burned in the previous stroke ignites and burns the unburned gas in the next stroke. Therefore, there is no need to install an electric spark plug.

Although the rotary engine can be air-cooled, the example shows a water-cooled rotary engine.
The rotor housing 3 has a water jacket 3E extending around the inner circumferential wall in the axial direction.

FIG. 8 shows the so-called PV diagram of the rotor engine of the present invention, where S ₁ is the mechanical compression stroke determined based on the mechanical structure of the vane rotary mechanism, and S ₂ is 1 This is an irreversible gas compression stroke carried out by the backflow of burned high-pressure gas from the previous stroke, and _S3 is a mixed combustion stroke. Combustion gas corresponding to the amount of gas generated by the combustion process is returned to the previous stroke as a reaction reflux, and combustion is completed.

Also, S ₄ is an irreversible ignition backflow process in which the gas after combustion flows into the gas chamber of the next stroke and ignites, and S ₅ is the process in which the gas in the next stroke is combusted. _S6 is the subsequent mechanical expansion stroke, and when the expansion stroke is completed, the pressure reaches approximately atmospheric pressure and is exhausted.

The PV cycle is a cycle that has the advantages of the Otto cycle and the Brayton cycle shown in FIGS. 9 and 10, and can be called a burnt gas mixture ignition combustion cycle.

<Embodiment - Effect> In the above configuration, when the rotor 2 is started and rotated by the starter as appropriate when starting the engine, the premixed gas of air and fuel sucked into one chamber R from the intake port 3A through the carburetor as appropriate. As the rotor 2 rotates in the direction of the arrow in FIG. 2, that is, clockwise in the diagram, it enters the compression stroke following the suction stroke from 0° in the diagram, and the chamber R moves to 1 in the diagram.
When reaching 2R and communicating the glow plug 3D with the attached communication groove 3C, the premixed gas is ignited and burned by the glow plug 3D.

Then, this ignited and combusted gas reaches the next stage chamber 12R and connects to the communication groove 3C, and the next burnt gas chamber 11 and the new unburned gas chamber are in communication. The high-pressure burnt gas flows into the unburnt gas chamber forming a strong vortex and mixes with the unburnt gas.
together and ignite.

When the pressure in this combustion chamber 12R rises rapidly during the combustion stroke, part of the combustion gas flows back through the passage 3C to the front chamber 11 at the beginning of the expansion stroke as a reaction reflux of the amount of backflow gas from one process before. The pressure and temperature of the front chamber 11 are increased again.

Then, as the rotor 2 rotates further and the phase advances, the chamber 12R becomes the 11R chamber in the next phase, and the premixed gas ignition is performed in the same way.In this process, the glow plug is deenergized and the fuel is not ignited. It is achieved only by autoignition and rotates according to the cycle.

In the process of one rotation of the rotor 2, each vane 5 contacts the inner circumferential surface 3' of the rotor housing 3 in various postures as described above. The communicating small holes 5d continue to take either a posture of communicating with the low-pressure side chambers 7R, 9R, or being closed by the inner circumferential surface 3' of the rotor housing 3.

Therefore, as described above, a force is always applied to the vane 5 toward the side housing 6 on both sides, and as a result, the side seal of the vane 5 is maintained well.

Further, as described above, the sealing of the tip surface 5e of each vane 5 against the inner circumferential surface 3' of the rotor housing 3 is achieved by the introduction pressure from the leading edge side groove 5a, the pressing force by the tip low pressure surface of the trailing side surface, and , sealed by centrifugal force.

Then, at the end of the 210° explosion stroke, the gas is exhausted from the exhaust port 3B.

It goes without saying that the embodiments of the present invention are not limited to the above-mentioned embodiments. For example, a rotor may be used in which burnt gas flows into the combustion chamber from both sides and forms a symmetrical vortex flow to perform combustion. Various embodiments can be adopted, such as forming a combustion chamber.

<Effects of the Invention> As described above, according to the present invention, the heat cycle of a rotary engine basically changes almost in a constant volume manner during ignition and combustion, and when the exhaust gas pressure is designed to atmospheric pressure, the low-temperature heat radiation stroke Since it is possible to create a cycle that combines the advantages of the Otto cycle and Breaton cycle in that they perform low pressure changes, it can be used for intermittent combustion Otto cycle engines and continuous combustion Breaton cycle engines with the same compression ratio. In comparison, not only is the thermal efficiency dramatically improved, but conversely, a highly efficient thermal cycle can be obtained at a low compression ratio, which is an excellent effect.

In terms of structure, first of all, the top seal and side seal of the vane, especially the gas pressure difference, are used, so the sealing effect is large, gas leakage loss is reduced, and the rotation to the rotor after the explosion stroke is As the angle changes, the position of the vane tip surface in contact with the inner surface of the rotor housing changes, resulting in an excellent effect that is advantageous in terms of strength design of the rotor and vanes.

That is, since the rotor and vanes receive a large external force during the suction, compression, and explosion strokes when the rotor rotation angle ranges from 0° to 210°, the distance between the vanes should be as short as possible, and the protrusion of the vanes should be kept as short as possible. We can deal with the fact that it is desirable that the length be as short as possible,
In addition, during the explosive expansion and exhaust strokes, the external force applied to the rotor and vanes rapidly decreases, and it is desirable that the volume of the chamber formed between each vane be as large as possible. It has the effect of being small.

Furthermore, the structure satisfies considerable engine design requirements; the position of the tip surface of the vane in contact with the inner surface of the rotor housing hardly changes from the suction and compression stroke to the explosion stroke, but after the explosion stroke, the position of the vane tip surface that contacts the rotor housing The position of the vane tip surface in contact with the inner surface changes significantly to the trailing side or the leading side, and the length of the vane protruding from the rotor also increases, reducing the vane support length. In addition to promoting an increase in the volume of the chamber between the vanes, there is also the effect of reducing the difference between the required support strength of the vanes in the suction compression and explosion strokes and the expansion and the necessary support strength of the vanes in the exhaust stroke.

In addition, by making it possible to combine a straight output shaft and a right cylindrical rotor, design and work are easy, and in particular, it is possible to combine a straight output shaft with a right cylindrical rotor. Unlike a rotary engine, there is almost no mass that moves eccentrically, so the vibration components in the vertical and horizontal directions are extremely small.Therefore, in addition to having the characteristic of low vibration, it is possible to attach many vanes. Is there a lot of cycles while the rotor is rotating?
Furthermore, it is easy to design and manufacture a high-output engine with extremely small output torque fluctuations, and the manufacturing cost is also low.

As mentioned above, since the structure is simple, failures are rare, repairs are easy, and there are advantages in maintenance management and maintenance.

Furthermore, by introducing the burnt gas back into the chamber at the end of the compression stroke, gas compression by the burnt gas is performed in addition to mechanical compression, resulting in a high effective compression ratio. Not only is it possible to ignite naturally, it eliminates the need for a spark-type electric ignition plug, which means that manufacturing costs are low, there is no radio interference, and the mechanical compression process can be Since it is possible to reduce the compression ratio, it is possible to use low-quality fuel with a low octane value such as kerosene, which has the advantage of being suitable for light engines for use in agriculture, construction, etc.

By providing a groove on the side surface of the vane that communicates only with low-pressure gas, a pressure difference is created even when the vane is pushed sideways by high-pressure gas, and the gas is sealed while the surrounding air is This has the effect of reducing sliding resistance with the side housing and ensuring smooth rotation.

In addition, the ignition performance is excellent due to the strong vortex caused by the jet of burned high-pressure gas and the combustibility of the burned gas.

And, by having excellent ignition performance,
It becomes possible to combust an ultra-lean mixture that cannot be ignited using normal combustion methods, and has the effect of enabling good combustion that can deal with exhaust pollution.

Furthermore, since the advantages of the Otto cycle and the Brayton cycle can be combined, it has the effect of achieving higher thermal efficiency than a reciprocating gasoline engine.

Furthermore, the inflow speed of the intake premixed gas is always constant, while the exhaust pressure is set to atmospheric pressure, which eliminates exhaust gas vibration and significantly reduces intake and exhaust noise. be.

In addition, since there is no valve mechanism or gear mechanism, it is advantageous in terms of generating mechanical noise.

In addition, the clearance for absorbing the difference in thermal expansion between the vanes and the rotor housing can be increased, making it possible to design a design that is long in the axial direction and small in the radial direction, resulting in a smaller overall size. In addition, the effect that the magnitude of the centrifugal force applied to the vanes can be made relatively small can also be achieved.

[Brief explanation of the drawing]

The drawings show one embodiment of the invention,
Fig. 1 is a general schematic vertical sectional view, Fig. 2 is a cross-sectional half-sectional view taken along the - line and '-' line in Fig. 1;
Figure 3 is a front view of the vane, Figure 4 is the same as in Figure 3.
5 is a side view of FIG. 3, FIGS. 6 and 7 are sectional views of changes in the contact position between the vane tip surface and the inner peripheral surface of the rotor housing as the rotor rotation angle changes, and FIG. 8 is a side view of the invention. Figures 9 and 10 are graphs of the Otto cycle and Brayton cycle. 2... Rotor, 5... Vane, R... Chamber, 3... Rotor housing, 5e... Tip (surface), 3'... Inner peripheral surface, 5c... Groove, 6... Side housing, 3C... Gas passage. 〓〓〓〓

Claims (1)

[Claims] 1. A substantially cylindrical rotor that rotates in a fixed direction, a large number of vanes that are supported by the rotor so as to protrude from its outer circumferential surface and are movable in the radial direction of the rotor, and A large number of chambers having an asymmetrical circumferential contour, sliding on the rotor, formed in an elliptical shape, moving in the rotational direction of the rotor together with the outer circumferential surface of the rotor and the vanes, and capable of freely increasing the volume of the exhaust stroke by being compressed and fixed. and a side housing that closes both sides of the rotor housing and slides into contact with both sides of the vane, wherein the tip of the vane is oriented in the opposite direction to the rotational direction of the rotor. The distal end surface in contact with the inner peripheral surface of the rotor housing is formed into a curved surface having a larger curvature than the curvature of the rotor housing, and is symmetrical with respect to a surface disposed passing through the axis of the rotor. The first half of the arc is in contact with the inner peripheral surface of the housing during the compression stroke, and the second half is in contact with the inner peripheral surface of the housing during the expansion stroke, so that the side surface of the vane always communicates only with the low-pressure side chamber. A rotary engine characterized in that a groove is provided and the vane has a split structure to allow slight movement toward the side housings on both sides.