JP2631626B2 - Rotary engine - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a rotary engine.

[0002]

2. Description of the Related Art A rotary piston engine has a less reciprocating motion than a reciprocating engine mechanism comprising a cylinder and a piston, and is considered to be advantageous as a prime mover, and various methods have been proposed. However, in 1954 the NS
Until the announcement of the so-called Wankel engine by U and Felix Wankel, there was no rotary engine that could be used in practice. After that, various car manufacturers until today,
The prime mover maker manufactures rotary engines and puts them on the market, but only those that are mass-produced are marketed as automobile engines by Mazda Motor Corporation (formerly Toyo Kogyo).

The basic structure of a rotary engine will be described below with reference to FIGS. The peritrochoid, which forms the contour of the peripheral (inner peripheral wall) of the rotor housing, is a trajectory drawn by the tip of the arm fixed to the rolling circle when the rolling circle inscribes the outer circumference of the fixed base circle and rolls. Is defined as The housing of the rotary engine includes a rotor housing 2 and a pair of side housings 4, and a rotor 6 is arranged in the housing. The rotation and revolution period of the rotor 6 in the housing are regulated by the external gear 8 fixed to the side housing 4 and the internal gear 10 fixed to the rotor 6 meshing with the external gear 8. According to the definition of the peritrochoid, constrictions 2b and 2c are formed on the short axis in the contour of the peripheral 2a of the rotor housing 2. When the rotary engine is driven, the rotor 6 holds the apex seal, that is, the seal 1
2 while rotating and revolving while making line contact with the peripheral 2a. The rotor housing 2 has an intake port 1
4. An exhaust port 16 is provided, and spark plugs 18 and 20 are provided. In the center hole of the rotor 6, a cylindrical portion 26 of the main shaft 26 is inserted via a rotor bearing 22.
The outer peripheral surface of the main shaft 26a is rotatably fitted, and the shaft portion 26b of the main shaft 26 eccentrically and integrally fixed to the cylindrical portion 26a is rotatably mounted on the side housing 4 via the main bearings 28 and 30. It is supported.

[0004]

The advantages of a rotary engine over a reciprocating engine are: a. Easy to balance inertia. b. Intake and exhaust valves are not required, and intake and exhaust timing is not disturbed. c. Low resistance to intake and exhaust. d. The outer dimensions are smaller and the weight is smaller than the working chamber volume. e. Suitable for high-speed rotation for high output.

On the other hand, the disadvantages are: a. When the intake and exhaust ports are peripheral ports, the operating strokes are likely to overlap. That is, the exhaust starts before the expansion ends, or the intake starts before the exhaust ends. b. Since the apex seal is basically in line contact with the rotor housing, blow-through occurs in other working chambers when straddling the ignition plug, the fuel injection nozzle or the intake / exhaust port. c. Since the rotor housing is confined on the short axis, especially at the compression top dead center, as shown in FIG.
And N2. Further, the surface area S is larger than the compression volume V, which is almost twice as large as that of a reciprocating engine having the same volume. In particular, low rotational speed, low load (in the case of idling and sloppy operation in the case of a car), rotational fluctuation such as misfire is likely to occur, and in order to prevent it, in the case of the Otto system (gasoline engine), the mixing ratio is made more "rich" With more fuel)
Must be. d. When the air-fuel ratio becomes "rich" due to the size and flatness of the specific surface area of the fuel chamber, the ratio of the residual and unburned gas increases, and the fuel efficiency deteriorates. e. When the theoretical compression ratio (upper limit of the compression ratio) is low and the trochoid constant K considered to be practically suitable is 6 to 8, the compression ratio is 15 to
21. At compression top dead center due to constriction of the rotor housing, a recess 32 is made in the arcuate profile of the rotor to prevent the combustion chamber from splitting, but of course this volume is not included. Therefore, a high compression ratio (18 or more) necessary for compression ignition (dieselization) is practically impossible. The trochoid constant K is defined as follows. When the length from the center of the rotor to the top of the rotor is R, and the revolving radius of the rotor that revolves while rotating is e (the amount of eccentricity with respect to the main shaft of the rotor), K = R / e f. Since the four strokes of suction, compression, combustion expansion, and exhaust are performed at specific locations in the rotor housing, the temperature of the engine body is largely biased, making it difficult to take measures against thermal stress.

[0006] As described above, a rotary engine having a number of features has been prevented from spreading.
It seems that the biggest cause is that the efficiency (fuel efficiency) is somewhat worse than that of the reciprocating engine, and that the diesel engine cannot be used practically. Therefore, an object of the present invention is to improve the fuel efficiency of a rotary engine, including the possibility of realizing a diesel system. To achieve the above object, the above a, b, c, d,
The disadvantages of e and f may be removed as shown below.

A. In order to prevent the intake and exhaust from overlapping, there is a method of making the intake air in the side housing. As a result, the gas seal (airtightness) is improved, and the blow-by of gas when the ignition plug and the injection nozzle hole and the seal body straddle the intake / exhaust port can be prevented. b. At the compression top dead center and the exhaust top dead center, in order to prevent the combustion chamber from being divided at the compression top dead center by the constrictions 2b and 2c on the short axis of the rotor housing, a recess 3 is formed in the rotor bow-shaped contour.
2 instead of eliminating the constriction on the short axis of the rotor housing. Also, the rotor is closely attached to the rotor housing at the compression top dead center and the exhaust top dead center, particularly at the compression top dead center (producing a squish area) by protruding the arcuate contour peripheral surface portion of the rotor. Then, by forming a compact (small S / V ratio) recess at an appropriate position on the rotor and causing the compressed air-fuel mixture to generate a larger swirl, the residual unburned gas is reduced, and a larger compression ratio (Otto system) is used. :
In the case of electric spark ignition), knocking at low rotation and high load can be prevented. c. By changing the depth of the dent of the rotor according to the load variation (by changing the mechanical compression ratio), high efficiency can be achieved under all conditions of low rotation high load and low load, high rotation low load and high load. Can be demonstrated. d. According to the above items b and c, even in lean burn for low fuel consumption (lean burn), further lean burn can be performed stably and easily. e. Since the rotary engine performs each stroke at a specific place in the rotor housing, in the case of partial load (low load), to reduce pumping loss in the intake stroke,
Install a "waist port" (exit) at a suitable place where the compression stroke of the rotor housing is performed without closing the throttle valve. If the waist port is controlled so that the waist port closes when the compression stroke has proceeded appropriately, the intake loss (pumping loss) can be reduced, and the combustion and expansion stroke can be made larger than the compression stroke, further improving the efficiency. .

[0008]

(1) In order to solve the above problems, the present invention provides a rotor housing having an opening for an intake port / exhaust porter and a spark plug and side housings disposed on both sides of the rotor housing. And an external gear fixed to the side housing, three tops, three arcuate peripheral surfaces formed between the tops, and a combustion chamber open to the peripheral surface. A rotor disposed in the housing, an internal gear fixedly mounted at the center of a side surface of the rotor so as to mesh with the external gear, a cylindrical portion rotatably fitted to the center of the rotor, and the cylindrical column; A shaft part eccentric with respect to a part, comprising a main shaft rotatably supported at the center of the external gear in the side housing, the inner peripheral surface of the rotor housing and the side surface. House By the suction, compression, combustion expansion, and exhaust strokes performed in the working chamber surrounded by the inner wall surface of the rotor and each peripheral surface of the rotor, the rotor is restricted by the external gears and the internal gears in the housing. In a rotary engine that revolves while revolving, the cross-sectional shape of the peripheral surface of the rotor housing is an ellipse without constriction on the short axis, and the curvature of each peripheral surface of the rotor is set on the short axis of the rotor housing. A seal body is disposed on each top of the rotor so as to be substantially slidable in the radial direction and urged in the radial direction while being substantially matched with the curvature of the constricted peripheral surface, and the top of the rotor is short of the rotor housing. The seal body slides in the radial direction when moved to the circumferential surface portion on the shaft, and a contact state of each top of the rotor with the circumferential surface of the rotor housing via the seal body. To be held, the sealing body was formed in the rotor top moth
Slidably fits radially into the guide hole and radially
And the piece holder urged to
Rotatable in a plane parallel to the side housing
Oscillating peak held and mounted on its surface with an arcuate leaf spring
And the surface of the oscillating piece is
Surface contact with the surrounding surface of the housing,
Roller bearings are provided rotatably, together with the leaf spring
The roller bearing inside the rotor housing
It is made to contact the peripheral surface. (2) In order to solve the above problems, the present invention provides a variable compression mechanism for changing the volume of the combustion chamber by an external driving force, and the variable compression mechanism is provided with the internal teeth of the rotor.
It is rotatably supported on the side opposite to the gear mounting side,
A second internal gear having the same diameter and the same number of teeth as the internal gear was formed.
A ring, and the external teeth of the pair of side housings.
Rotatable on the side housing opposite to the gear fixed side
The external gear supported and meshed with the second internal gear
A tubular body having a second external gear having the same diameter and the same number of teeth,
A method of forming the bottom of a combustion chamber and varying the volume in the combustion chamber
A piston movably supported in the combustion chamber,
The rotational movement of the ring translates the linear movement of the piston.
Said tubular body comprising a motion converting mechanism for converting into motion.
Is rotated by a driving force outside the housing.
The combustion chamber is moved by moving the piston by rotation of the tubular body.
Is changed . (3) In order to solve the above problem, the present invention opens a plurality of waist ports located on the downstream side of the intake port and controlled to be opened / closed by a control valve on an inner peripheral surface of the rotor housing. A port communicates with the intake port via a chamber formed in the housing.

[0009]

[Action]

(1) At the compression top dead center and the exhaust top dead center, particularly at the compression top dead center, the peripheral surface of the rotor is in close contact with or close to the inner peripheral surface of the rotor housing, a large compression ratio is obtained, and the unburned gas is reduced. In addition, knocking does not occur at low rotation and high load. (2) The gas contact is improved by the surface contact of the rocking piece surface with the inner peripheral surface of the rotor housing, and when the rocking piece straddles the spark plug or the injection nozzle hole or the suction / exhaust port, the top of the rotor is Gas does not blow through between the working chambers as boundaries. (3) When the oscillating piece moves at high speed along the inner peripheral surface of the rotor housing, the sliding resistance is reduced by the roller bearing, and the oscillating piece smoothly contacts the outer peripheral surface of the rotor housing at a high speed. Move with. (4) By changing the compression ratio, it is possible to always operate with high efficiency from low rotation to high rotation and from low load to high load. (5) When the rotor rotates, the relative positional relationship between the rotor and the ring does not change. When this ring is rotated by rotating the second external gear by an external operating force,
As the piston moves, the volume of the combustion chamber that opens to the rotor peripheral surface changes. (6) When the control valve of the waist port is opened in order from the intake port in accordance with the load, the intake air is discharged from the working chamber until the seal body passes through the opened waist port, and is substantially in the compression stroke. Is controlled.

[0010]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS The construction of the present invention will be described below in detail with reference to embodiments shown in the accompanying drawings. In FIG. 6, reference numeral 34 denotes a rotary engine housing, which includes a rotor housing 36 and side housings 38 and 40. The inner peripheral wall surface (peripheral surface) of the rotor housing 36 has a central vertical cross-sectional shape formed into an ellipse having no constriction on the short axis. In the present invention,
The peripheral surface of the ellipse is configured so that its tangent does not enter the inside of the ellipse, and the curvature near the minor axis of the ellipse, when the top of the rotor 42 is located on the minor axis of the peripheral surface, An appropriate value is set so that the gap formed between the top and the peripheral surface does not become too large. Tubular bodies 44, 46 are coaxially supported on the side housings 38, 40, respectively. The flange of one tubular body 44 is fixed to the side housing 38,
The outer peripheral surface of the other tubular body 46 is
It is rotatably fitted in the hole 0 so as not to shift in the axial direction. Reference numeral 52 denotes a main shaft, which is composed of a cylindrical portion 52a and a shaft portion 52b eccentric to the cylindrical portion 52a.

The outer peripheral surfaces of the shaft portion 52b of the main shaft 52 are provided on the inner diameter portions of the tubular bodies 44, 46 with the main bearings 48,5.
0 and freely fit through. The column portion 52a
Is rotatably fitted in a central hole of the rotor 42 via a metal bearing. On one side of the tubular body 44, an external gear 56 for regulating the rotation and the revolution period of the rotor 42 is fixed. 59 is the rotor 4
2 is an internal gear for regulating the rotation and revolving, and is fixed to the center of the side surface of the rotor 42. The external gear 56 meshes with the internal gear 59. A piston head 42a comprising an arcuate contour of the rotor 42,
42b and 42c are set to be the same as the curvature of the peripheral surface near the short axis. As a result, as shown in FIG. 1 and FIG. The rotor housing 36 is in close contact with a peripheral surface near the short axis. A guide hole 58 having a guide surface is formed at each of the three top portions of the rotor 42 in a radial direction, that is, along a line segment connecting the center of the rotor 42 and each of the top portions. 60 is slidably held in the guide hole 58.

The piece holder 60 is shown in FIGS.
As shown in FIG. 0, the front and rear surfaces are formed in a box shape, and come into contact with the guide surfaces 58a and 58b of the guide holes 58, the both side surfaces that come into contact with the inner wall surfaces of the side housings 38 and 40, and the bottom surface and the piece holding surface 60a. It is configured. The piece holder 60 is composed of two parts 60b and 60c, which are meshed and connected as shown in FIGS. By the sliding action of the convex portion and the concave portion of the comb-like connecting portion, the part 60
5, b and 60c are configured to be expandable and contractible in the left-right direction, that is, the thickness direction of the rotor 42, and the parts 60b and 60c are separated from each other along the guide of the comb teeth by a spring force (not shown). Biased in the direction.
With this urging force, both side surfaces of the piece holder 60
It comes into close contact with the inner wall surfaces of the side housings 38, 40.
Both side surfaces of the piece holder 60 can function as a piston ring. The piece holding surface 60a
Is composed of a concave curve having an arcuate cross section, and
The bottom projecting portion is rotatably tightly fitted in a plane parallel to the inner wall surfaces of the side housings 38, 40.

The surface of the swinging piece 62 is composed of a surface plate 62a having an arcuate cross section, and a leaf spring 62b having an arcuate cross section with one side portion K fixed to the surface plate 62a. The curved surface is raised by a predetermined distance from the curved surface of the surface plate 62a. Openings are formed on both sides of the surface plate 62a, and the opening is formed, and a pair of roller bearings 68 and 70 rotatably supported in the swinging piece 62 are respectively disposed in the openings. ing. The roller bearings 68 and 70 are rotatably supported around an axis perpendicular to the inner wall surfaces of the side housings 38 and 40, and their surfaces are the same as the surface plate 6.
It is arranged slightly protruding from the surface of 2a. The surface of the leaf spring of the swinging piece 62 is
The roller bearings 68, 68 are resiliently urged by a spring (not shown) which urges the rotor 42 on the extension of the axis connecting the center of the rotor 42 and the vertex of the rotor 42, that is, in the radial direction of the rotor 42.
Together with 70, it is in surface contact with the peripheral surface of the rotor housing 36.

As shown in FIG. 11, gas seals 72 and 74 are provided in front and rear of the surface plate 62a so as to be urged in the protruding direction, and mainly serve the gas seal between the swinging piece 62 and the peripheral surface. ing. Reference numerals 64 and 66 denote gas seals disposed on both side surfaces and the bottom surface of the swinging piece 62. The gas seals are mainly provided between the swinging piece 62 and the side housings 38 and 40 and between the swinging piece 62 and the piece holder 60. Responsible for gas seal between. 8 and 9, a corner seal 76 is provided for eliminating a break between a holder line seal 78 provided on the guide surface of the guide hole 58 and an arcuate line seal 80 provided on both side surfaces of the rotor 42. It is urged by a spring 82 in the projecting direction. The piece holder 60 and the swinging piece 62
It constitutes a seal body. In carrying out the present invention, a conventional line contact type apex seal is used for the seal body.
This may be configured to be slidable in the radial direction of the rotor and biased in the radial direction.

In the present invention, the rotor housing 36
Has no constriction on the peripheral surface. Therefore, in order to bridge the expansion of the gap between the top of the rotor 42 and the peripheral surface when the swinging piece 62 passes through the peripheral surface on the short axis, the piece holder 60 is moved radially along the guide surface of the guide hole 58. Slide to. The holder line seal 78 is responsible for the gas seal on the slide surface at this time. The arcuate line seal 80 is provided between the rotor 42 and the side housings 38 and 40.
Responsible for gas seal with inner wall of

Next, the variable compression mechanism will be described with reference to FIGS. In the present invention, variable compression is
This is done by changing the volume of the combustion chamber 84 provided on each of the three arcuate surfaces between the three tops of the rotor 42, i.e., the piston heads 42a, 42b, 42c. The variable compression mechanism of each piston head 42a, 42b, 42c
This mechanism converts the rotation of the gear 86 shown in FIG. 6 into a linear movement of the piston 88, and this mechanism is the same. 90 is the piston head 42a, 42b, 42c
Each of the cylinders is fixed to the rotor 42 and is opened on the surface of the rotor 42. Reference numeral 92 denotes a screw shaft rotatably supported by the rotor 42 and movably in the axial direction, and a piston 88 disposed slidably and non-rotatably on the cylinder 90 is fixed to the screw shaft. The surface of the piston 88 and the cylinder 90
A recess surrounded by a circle constitutes a combustion chamber 84. Reference numeral 96 denotes a nut-type worm gear rotatably supported by the rotor 42 so as not to be displaced in the axial direction. A nut portion of the inner diameter portion is screwed to the screw shaft 92.

A shaft 94 is rotatably supported by the rotor 42 so as not to move in the axial direction thereof, and is disposed at right angles to the screw shaft 92. A worm 98 and a gear 86 are fixed to the shaft body 94,
The worm 98 meshes with the worm gear 96. Reference numeral 100 denotes a ring supported on the other surface of the rotor 42 so as to be rotatable so as not to move in the axial direction so as to be centered on one face of the internal gear 59 of the rotor 42, and two rings Internal gears 102 and 104 are provided. A gear 86 fixed to the shaft body 94 meshes with one of the internal gears 102. The other internal gear 10
4 has the same diameter and the same number of teeth as the internal gear 59. In the tubular body 46, the external gear 56 and the center,
An external gear 106 having the same diameter and the same number of teeth is formed, and the external gear 106 meshes with the internal gear 104.

Reference numeral 108 denotes a shaft rotatably supported by an appropriate fixing member (not shown), and is connected to a driving device (not shown) such as a motor controlled by a computer (not shown). A worm 110 is attached to the shaft 108.
The worm 110 is engaged with a worm gear 112 fixed to the tubular body 46. The above constitutes the variable compression mechanism, and the three gears 86 on the rotor 42 side
Are engaged with the internal gear 86 at an angular interval of 120 degrees. In FIG. 1, 114, 11
Reference numerals 6, 118, and 120 denote waist ports formed downstream of and adjacent to the intake port 122, and communicate with a chamber 124 formed in the rotor housing 36. The chamber 124 communicates with the intake port 122. ing. The waist ports 114, 116, 118, 1
20 has control valves V1, V2, V
3, V4 valve elements 126, 128, 130, 132 are arranged. The control valves V1, V2, V
3 and V4 are each connected to a drive device (not shown) controlled by a computer. Reference numeral 134 denotes an exhaust port, and 136 denotes a spark plug provided in the rotor housing 36. When the rotary engine is used as a diesel engine, the spark plug 13
A fuel injection nozzle is attached instead of 6.

Next, the operation of this embodiment will be described. Each surface of the rocking pieces 62 disposed at the three tops of the rotor 42 moves along the peripheral surface by the intake, compression, combustion, expansion, and exhaust strokes of the rotary engine while making surface contact with the peripheral surface. . In accordance with a change in the orientation of each top of the rotor 42 due to the rotation of the rotor 42, the swinging piece 62 moves relative to the piece holder 60 in a plane parallel to the inner wall surfaces of the side housings 38 and 40. Then, the surface of the swinging piece 62 is kept in contact with the peripheral surface.
The deviation of the curvature near the short axis and near the long axis of the peripheral surface is compensated by the elasticity of the leaf spring 62b on the surface of the oscillating piece 62, and good surface contact between the surface of the oscillating piece 62 and the peripheral surface is achieved. Is held. The theoretical gap formed between the surface of the swinging piece 62 and the peripheral surface on the short axis due to the removal of the constriction from the peripheral surface, as shown in FIGS. The holder 60 is removed by moving along the guide hole 58 of the rotor 42 by the spring force in the biasing projecting direction, that is, in the radial direction, and the surface contact between the surface of the swing piece 62 and the peripheral surface is maintained.

FIG. 1 shows one of the three piston heads 42a, 42b and 42c of the rotor 42.
A shows a state where a is located at the top dead center of the exhaust (exhaust completion point). FIG. 2 shows a state where the piston head 42a is located at the intake bottom dead center (intake completion point). FIG.
Means that the piston head 42a is at the compression top dead center (compression completion point)
Is shown. FIG. 4 shows a state in which the piston head 42a is located at the bottom dead center of combustion and expansion (expansion completion point). When driving a rotary engine,
Depending on the load, the waist control valves V1, V2,
V3 and V4 are controlled and waistports are 114 and 11
6, 118 and 120 are released in that order. As a result, the swinging piece 62 is moved to the opened waist port 114,1.
Until the air passes through 16, 118 and 120, the intake air is exhausted from the working chamber on the piston head through the chamber 124, and the intake air amount substantially used in the compression stroke is adjusted to an appropriate value.

During the rotation of the rotor 42, the rotation angle of the ring 100 with respect to the rotor 42 does not change. This will be described below. The rotation and revolution of the rotor 42 are regulated by the engagement between the internal gear 59 and the external gear 56. Therefore,
The internal gear 104 arranged on the other surface of the rotor 42 also has
It revolves along the same locus as the revolving cycle circle at the center of the internal gear 59. At this time, the internal gear 100 rotates along with its revolution by meshing with the external gear 106, and this rotation is synchronized with the rotation of the internal gear 59, that is, the rotation of the rotor 42. Therefore, the ring 100 is
During the rotation of 2, the rotor 42 remains stationary with respect to the rotor 42, and its rotation angle does not change with respect to the rotor 42.

Next, the variable compression operation will be described. When the shaft 108 rotates under the control of the computer, the rotation is performed by the worm 110 and the worm wheel 112, the external gear 106, the internal gear 104, the internal gear 86, and the gear 8.
6, transmitted to the nut-type worm gear 96 via the worm 98, and the nut-type worm gear 96 rotates. By this rotation, the screw shaft 92 moves in the axial direction, the piston 88 moves, and the volume of the combustion chamber 84 changes.
This displacement depends only on the rotational displacement of the shaft 108.

[0023]

According to the present invention, as described above, since the constriction of the rotor housing is removed, a high compression ratio can be realized. Further, since each top of the rotor is in surface contact with the rotor housing, the overlap of the intake and exhaust strokes can be reduced as compared with the conventional line contact. In addition, since the mechanical compression ratio can be freely changed according to the operating conditions, it is possible to always operate with high efficiency from low rotation to high rotation and from low load to high load.

[Brief description of the drawings]

FIG. 1 is a longitudinal sectional view of a rotary engine.

FIG. 2 is a longitudinal sectional view of a rotary engine.

FIG. 3 is a longitudinal sectional view of a rotary engine.

FIG. 4 is a longitudinal sectional view of a rotary engine.

FIG. 5 is a schematic external view of a swinging piece.

FIG. 6 is a longitudinal sectional view of the rotary engine cut from another direction.

FIG. 7 is a sectional view of a rotor.

FIG. 8 is a partial external view of a rotor.

FIG. 9 is a cross-sectional view of the rotor of FIG.

FIG. 10 is a sectional view of a swinging piece.

11 is a partial plan view of the swinging piece of FIG. 10 as viewed in the direction of arrow B. FIG.

12 is a side cross-sectional view of the swinging piece of FIG. 11 as viewed from the arrow direction C.

FIG. 13 is a bottom view of the piece holder.

FIG. 14 is a sectional view of a conventional technique.

FIG. 15 is a cross-sectional view of the prior art taken from another direction.

[Explanation of symbols]

 Reference Signs List 2 rotor housing 4 side housing 6 rotor 8 external gear 10 internal gear 2b constriction 2c constriction 12 seal body 14 intake port 16 exhaust port 18 spark plug 20 spark plug 22 rotor bearing 26 main shaft 28 main bearing 30 main bearing 32 recess 34 housing 36 Rotor housing 38 Side housing 40 Side housing 42 Rotor 44 Tubular body 46 Tubular body 48 Main bearing 50 Main bearing 52 Main shaft 56 External gear 58 Guide hole 59 Internal gear 60 Piece holder 62 Oscillating piece 64 Gas seal 66 Gas seal 68 Roller bearing 70 Roller bearing 72 Gas seal 74 Gas seal 76 Corner seal 78 Holder line seal 80 Bow line Seal 82 Spring 84 Combustion chamber 86 Gear 88 Piston 90 Cylinder 92 Screw shaft 94 Shaft 96 Nut-type worm gear 98 Worm 100 Ring 102 Internal gear 104 Internal gear 106 External gear 108 Shaft 110 Warm 112 Worm gear 114 Waist port 116 West Port 118 West port 120 West port 122 Intake port 124 Chamber 126 Valve element 128 Valve element 130 Valve element 132 Valve element 134 Exhaust port 136 Spark plug

Claims (4)

(57) [Claims] 1. A housing comprising: a rotor housing having an opening for an intake port / exhaust port and a spark plug; and a side housing disposed on both sides of the rotor housing; and an external gear fixed to the side housing. , 3
A rotor disposed in the housing having three tops, three arcuate peripheral surfaces formed between the tops, and a combustion chamber open to the peripheral surface; and the external teeth at a central portion of a side surface of the rotor. An internal gear fixedly engaged with the gear; a cylindrical portion rotatably fitted to the center of the rotor; and a shaft portion eccentric to the cylindrical portion, the shaft portion being attached to the side housing. A main shaft rotatably supported at the center of the external gear is provided, and the operation is performed in an operating chamber surrounded by the inner peripheral surface of the rotor housing, the inner wall surface of the side housing, and each peripheral surface of the rotor. A cross section of a peripheral surface of the rotor housing in a rotary engine in which the rotor revolves in the housing while rotating by being restricted by the external gear and the internal gear by suction, compression, combustion expansion, and exhaust strokes. Shape An elliptical shape with no constriction on the shaft, the curvature of each peripheral surface of the rotor is made substantially coincident with the curvature of the non-constrictive peripheral surface on the short axis of the rotor housing, and the rotor slides radially on each top of the rotor. A seal body is disposed freely and radially biased, and when the top of the rotor moves to a peripheral surface portion on a short axis of the rotor housing, the seal body slides in the radial direction to slide the rotor. A contact state of each top portion with the peripheral surface of the rotor housing via the seal body is maintained, and the seal body is provided on a guide formed on the rotor top portion.
Slidably fits radially into the hole and radially
An energized piece holder and the piece holder
It is rotatable in a plane parallel to the side housing.
Oscillating piece with a bowed leaf spring attached to the surface
And the surface of the swinging piece is
Surface contact with the peripheral surface of the jing, and
Roller bearings are provided rotatably and together with the leaf springs
The roller bearing is mounted on the inner periphery of the rotor housing.
A rotary engine characterized by being brought into contact with a surface . 2. The capacity of the combustion chamber is increased by an external driving force.
A variable compression mechanism that is rotatably supported on a side of the rotor opposite to the side where the internal gear is mounted, and has a second tooth having the same diameter and the same number of teeth as the internal gear. A ring on which the internal gear is formed, and the outer teeth rotatably supported on a side housing of the pair of side housings opposite to the side on which the external gear is fixed, and meshing with the second internal gear. A tubular body having a second external gear having the same diameter and the same number of teeth as a gear, and a piston that constitutes the bottom of the combustion chamber and is supported in the combustion chamber so as to be movable in a direction in which the volume in the combustion chamber is variable; A motion conversion mechanism that converts the rotational motion of the ring into a linear motion of the piston, and rotates the tubular body by a driving force external to the housing, and rotates the piston by the rotation of the tubular body. Move and said Rotary engine according to claim 1, characterized in that so as to vary the volume of the baking chamber. 3. A plurality of waist ports located on the downstream side of the intake port and controlled to be opened and closed by a control valve are opened on an inner peripheral surface of the rotor housing,
The rotary engine according to claim 1, wherein each of the waist ports communicates with the intake port via a chamber formed in the housing. 4. A housing comprising a rotor housing having an opening for an intake port, an exhaust port and a spark plug, and side housings disposed on both sides of the rotor housing, and an external gear fixed to the side housing. ,
A rotor disposed in the housing having three tops, three arcuate peripheral surfaces formed between the tops, and a combustion chamber open to the peripheral surface; An internal gear fixed to mesh with the tooth gear; a cylindrical portion rotatably fitted to the center of the rotor; and a shaft portion eccentric to the cylindrical portion, the shaft portion being attached to the side housing. A main shaft rotatably supported at the center of the external gear, and provided in an operating chamber surrounded by an inner peripheral surface of the rotor housing, an inner wall surface of the side housing, and each peripheral surface of the rotor. In a rotary engine in which the rotor is revolved in the housing while being rotated by the external gear and the internal gear by the suction, compression, combustion expansion, and exhaust strokes, the volume of the combustion chamber is increased. By the driving force of A variable compression mechanism, which is rotatably supported on the side of the rotor opposite to the side where the internal gear is mounted, and has a second tooth having the same diameter and the same number of teeth as the internal gear. A ring on which an internal gear is formed, and the external gear that is rotatably supported by a side housing of the pair of side housings that is opposite to the external gear fixed side and meshes with the second internal gear. A tubular body having a second external gear having the same diameter and the same number of teeth, a piston constituting the bottom of the combustion chamber and supported in the combustion chamber so as to be movable in a direction in which the volume of the combustion chamber is varied; A motion conversion mechanism for converting the rotational motion of the ring into a linear motion of the piston, wherein the tubular body is rotated by a driving force external to the housing, and the piston is moved by the rotation of the tubular body. And the combustion Rotary engine is characterized in that so as to vary the volume.