JP5480730B2 - Airtight structure of vane type internal combustion engine - Google Patents

Description

  The present invention relates to an air-tight structure of a vane-type internal combustion engine for the purpose of improving the air-tightness of a vane and reducing friction by using high-pressure combustion gas generated in an explosion stroke of the vane-type internal combustion engine.

  Conventionally, in a vane type internal combustion engine, a groove sliding portion into which a vane and a vane are inserted, or a vane tip sliding with a housing inner peripheral surface, keeps airtight against high-temperature combustion gas generated by a combustion process. Various seals have been proposed.

  Patent Document 1 describes a structure in which both side surfaces of a vane called a partition plate are sandwiched between semi-cylindrical seals and pressed with a spring, and a seal is inserted into a groove at the tip of the partition plate and pressed with a spring. Has been.

  Japanese Patent Application Laid-Open No. H10-228561 describes a technique in which a tip vane is provided at the tip of the vane and is pressed against the inner surface of the housing with a spring.

  The present applicant has applied for Patent Document 3 regarding a vane type internal combustion engine.

Japanese Patent Laid-Open No. 2001-115849 JP-A-10-68301 Japanese Patent Laid-Open No. 2008-45513

  However, the airtight holding system of the vane type internal combustion engine described in Patent Documents 1 and 2 has a complicated structure and poor airtight performance. Although it is pressed and pressed by a spring, it is in a part affected by high-temperature combustion gas generated by the combustion process, and there remains a problem that the spring load greatly decreases due to heat sag, which can be realized. It was difficult. Furthermore, it has been desired to realize a maintenance-free internal combustion engine that does not use lubricating oil.

  In the rotary engine of Patent Document 1, it is presumed that 3 or more springs are used per vane, and a large number of 15 or more springs are used per rotor. Furthermore, the seal material is unknown and no measures for preventing the leakage of lubricating oil related to the seal are taken into consideration.

  The vane in the vane rotary internal combustion engine of Patent Document 2 requires a high accuracy of machining because the shape of a part requiring dimensional accuracy, such as a guide body or a groove into which a tip vane is inserted, is required. Is a large number of 16 and the cost is high. In this structure, the lubricating means is absolutely necessary, but it is difficult to realize.

  The vane type internal combustion engine of Patent Document 3 also has room for improvement with respect to the seal.

  The present invention solves the above-described problems and provides a hermetic structure for a vane type internal combustion engine that improves the airtightness of the vane and has a simple structure with little friction and no maintenance oil without using lubricating oil. The purpose is to do.

According to the first aspect of the present invention, the housing, the rotor built eccentrically with respect to the axial center of the housing and rotatable in the housing, the plurality of vanes in sliding contact with the inner peripheral surface of the housing, and the vanes there a gas-tight structure of the vane-type internal combustion engine having a plurality of vane groove to slide, wherein the the rotor, the pressure gas distribution passage arranging a plurality of flowing a high pressure combustion gas generated by the explosion stroke The pressure gas distribution passages are formed in communication with each other on the axial center side of the rotor, and are formed in communication with the vane grooves, between the vane grooves on the outer peripheral surface of the rotor. Each of the pressure gas distribution passages is formed with an inflow portion through which the high-pressure combustion gas flows, and each of the inflow portions has a flow passage in the pressure gas distribution passage and the vane groove. Disposed check valve structure for maintaining the force, within the vane, along a radial direction of said rotor, gas passage combustion gas of the high pressure through the vane grooves and the communication flows is formed, the A vane tip seal is fitted into an end portion of the gas passage on the inner peripheral surface side of the housing, and a tip portion of the vane tip seal is formed in an arc shape protruding toward the inner peripheral surface side of the housing, and the high pressure The combustion gas flows into the pressure gas distribution passages and flows into the vane grooves communicating with the pressure gas distribution passages to press the vanes against the inner peripheral surface of the housing. And

  According to a second aspect of the present invention, the vane has a rectangular flat plate shape, and an end surface on the inner peripheral surface side of the housing is formed perpendicular to the radial direction of the rotor, and is an angle located inside the region where the explosion stroke is performed. The portion is formed so as to be in sliding contact with the inner peripheral surface of the housing during the explosion stroke.

According to a third aspect of the present invention, the vane is provided with a vent hole communicating the gas passage and the vane groove.

According to a fourth aspect of the present invention, the check valve structure is inserted into the inflow port portion and communicates with the pressure gas distribution passage so that the high-pressure combustion gas can flow therethrough, and the valve A valve fixing member arranged on the inner peripheral surface side of the housing from the main body so as to be able to flow in or seal the high-pressure combustion gas; and a sphere housed in a gas passage formed in the valve main body; And the sphere located in the region where the explosion stroke is performed moves to the pressure gas distribution passage side during the explosion stroke and causes the high-pressure combustion gas to flow into each pressure gas distribution passage, The sphere of the check valve located in a region contacts the valve fixing member to seal the high-pressure combustion gas.

The invention according to claim 5 is characterized in that a member in which carbon is impregnated with metal is used for the vane and the vane tip seal.

  According to the first aspect of the present invention, the rotor is provided with pressure gas distribution passages through which high-pressure combustion gas flows, and the pressure gas distribution passages communicate with each other on the axial center side of the rotor. In addition to the formation, the vane grooves are formed so as to communicate with each other. Between the vane grooves on the outer peripheral surface of the rotor, an inlet portion is formed which communicates with the pressure gas distribution passage and into which high-pressure combustion gas generated by the explosion stroke flows.

  Since the vane is pressed against the inner peripheral surface of the housing using the high-pressure combustion gas generated by the explosion stroke, the airtightness of each divided region can be stably maintained.

In addition, a check valve structure for maintaining the pressure gas distribution passage and the pressure in the vane groove is disposed at the inlet portion. Thus, high-pressure combustion gas is taken into each pressure gas distribution passage and each vane groove during the explosion stroke, and high-pressure combustion gas is sealed in each pressure gas distribution passage and each vane groove during the other strokes. The pressure can be maintained, and the airtightness of each divided area can be maintained at all times. Further, a gas passage is formed in the vane along the radial direction of the rotor so as to communicate with the vane groove and into which high-pressure combustion gas flows, and at the end of the gas passage housing on the inner peripheral surface side, A seal is inserted, and the tip of the vane tip seal is formed in an arc shape protruding toward the inner peripheral surface of the housing. As a result, the vane tip seal is pressed against the inner peripheral surface of the housing by the high-pressure combustion gas flowing from the gas passage together with the pressure of the vane itself, so that the airtightness of each divided chamber is more reliably maintained. be able to. In addition, since the tip of the vane tip seal is formed in an arc shape, friction with the inner peripheral surface of the housing can be reduced, so that the sliding contact between the tip of the vane tip seal and the inner peripheral surface of the housing body is smooth. Can be.

  According to the second aspect of the present invention, the vane has a rectangular flat plate shape, and the end surface on the inner peripheral surface side of the housing is formed perpendicular to the radial direction of the rotor. It is formed so as to be in sliding contact with the inner peripheral surface of the housing during the stroke.

  As a result, the flow of high-pressure combustion gas generated during the explosion stroke is stopped at the corner of the vane that is in sliding contact with the inner peripheral surface of the housing, and prevents the vane from flowing around the corner of the vane. It can be prevented from being pushed into the rotor center side.

According to the third aspect of the present invention, the vent is provided in the vane so as to communicate the gas passage and the vane groove. As a result, the high-pressure combustion gas generated by the explosion process flows out into the gap between the vane and the vane groove, and the high-pressure combustion gas intervening in the gap floats the vane and causes friction between the vane and the vane groove. Can be reduced.

According to a fourth aspect of the present invention, the check valve structure is fitted into the inlet portion, and is connected to the pressure gas distribution passage so as to be able to flow high-pressure combustion gas. The valve fixing member is arranged on the inner peripheral surface side and is formed so that high-pressure combustion gas can flow in or seal, and a sphere housed in a gas passage formed in the valve body.

  The sphere located in the region where the explosion stroke is performed moves to the pressure gas distribution passage side during the explosion stroke and flows high-pressure combustion gas into each pressure gas distribution passage, and the sphere located in the other region becomes the valve fixing member. The high pressure combustion gas is sealed by contact.

  Thereby, the flow of the high-pressure combustion gas is switched by the movement of the sphere, and the pressure in each pressure gas distribution passage and each vane groove can be maintained, so that the airtightness of each divided chamber is always maintained. be able to.

In the invention according to claim 5 , a member in which metal is impregnated with carbon is used for the vane and the vane tip seal. By using a carbon member having self-lubricating properties, no lubricating oil is required, so that maintenance can be made free.

It is sectional drawing which shows the airtight structure of the vane type internal combustion engine by one Embodiment of this invention. It is a disassembled perspective view which shows the housing and rotor of the engine in FIG. It is a disassembled perspective view which shows the rotor and vane in FIG. FIG. 2 is a partial enlarged cross-sectional view of a chamber in an explosion stroke in FIG. 1. It is a partial expanded sectional view by the side of the inner peripheral surface of the housing main-body part of a vane. It is (a) partial expanded sectional view of a non-return valve, and is SS sectional drawing in (b) (a). It is explanatory drawing which shows the force of the combustion gas G of the airtight structure of this embodiment.

  An embodiment of an airtight structure of a vane type internal combustion engine according to the present invention will be described with reference to the drawings. An airtight structure (hereinafter referred to as an airtight structure) 100 of a vane type internal combustion engine 100 according to the present invention prevents pressure gas from leaking from a vane type internal combustion engine in which five vanes are mounted on a rotating rotor and is free from engine maintenance. It is what makes it possible.

  As shown in FIG. 2, a vane type internal combustion engine (hereinafter referred to as an engine) 1 in the airtight structure 100 of the embodiment is disposed on a substantially cylindrical housing body 31 and on both sides of the housing body 31. A housing 3 having a pair of side housing portions 32 and 32 for closing the opening portions at both ends of the housing main body 31; a rotor 5 built in the housing 3 and rotatable; and a vane 7 attached to the rotor 5; It has. As shown in FIG. 1, a hollow portion 60 is formed in the gap between the housing 3 and the rotor 5.

  As shown in FIGS. 1 and 2, the housing main body 31 has an inner peripheral surface 31 a that is formed in a true circle centered on the axis when viewed from the axial direction. Two built-up portions (first built-up portion 31b and second built-up portion 31c) are formed on the outer peripheral surface of the housing main body 31, and a boss portion 31d is formed between the two built-up portions. Is formed.

  As shown in FIG. 2, each side housing portion 32, 32 is formed in a disc shape, and is attached to the housing main body portion 31 so as to close the rotor 5 from the side surface. Each side housing portion 32, 32 is formed with support holes 32a, 32a for supporting the rotating shaft 14 of the rotor 5 described later, and arc holes serving as intake ports 18, 18, and exhaust ports 19, 19 described later. ing.

  As shown in FIGS. 2 and 3, the rotor 5 is formed in a cylindrical shape having a width substantially the same as the width (length in the axial direction) of the housing main body 31, and as shown in FIG. The portion 31 is arranged with a center of rotation at a position eccentric from the center position in the axial direction. As shown in FIGS. 2 and 3, a rotation shaft 14 serving as a power output shaft is disposed at the rotation center position of the rotor 5.

  As shown in FIGS. 1, 2, and 3, the rotor 5 has vane grooves 51 (51 a, 51 b, 51 c, 51 d) in which the vanes 7 slide radially from the rotating shaft 14 toward the radially outer side of the rotating shaft 14. , 51e) are formed. Each of the vane grooves 51 is formed at five positions over the entire width direction of the rotor 5 with the same angle therebetween. As shown in FIG. 1, the vane 7 (7a, 7b, 7c, 7d, 7e) is inserted into each vane groove 51.

  As shown in FIGS. 1, 2, and 3, five concave portions 53 (53 a, 53 b, 53 c, 53 d, 53 e) are formed on the outer peripheral surface 52 of the rotor 5 at equal angles. The concave portion 53 is formed by deeply cutting the rotation traveling direction side so as to be easily subjected to the pressure in the direction of rotation when receiving the pressure of the explosion in the explosion stroke described later (the direction in which the arrow in FIG. 1 rotates). Is).

  As shown in FIG. 1, a pressure gas distribution passage 54 (54a, 54b, 54c, 54d, 54e) through which high-pressure combustion gas (hereinafter referred to as combustion gas) G generated by an explosion stroke flows into the rotor 5. Is arranged from the outer peripheral surface 52 side of the rotor 5 toward the rotating shaft 14 side. Each pressure gas distribution passage 54 is arranged in communication with another pressure gas distribution passage 54 on the rotating shaft 14 side of the rotor 5. Each of the pressure gas distribution passages 54 on the front side in the rotational direction of the rotor 5 and each of the adjacent vane grooves 51 on the rear side in the rotational direction of the rotor 5 are arranged in a substantially Y shape when viewed from the axial direction of the rotor 5. ing. Each adjacent pressure gas distribution passage 54 and each vane groove 51 are formed to communicate with each other at the substantially central portion of each pressure gas distribution passage 54 and on the rotary shaft 14 side of the rotor 5 of each vane groove 51.

  As shown in FIG. 1, between the vane grooves 51 on the outer peripheral surface 52 of the rotor 5, the inlet portions 55 (55 a, 55 b, 55 c, 55 c, 55 b, 55 c, 55) communicate with the pressure gas distribution passages 54 and flow in the combustion gas G. 55d and 55e) are formed.

  As shown in FIG. 1, the check valve structure 8 (8a) that circulates and seals the combustion gas G to maintain the pressure in each pressure gas distribution passage 54 and each vane groove 51, as shown in FIG. , 8b, 8c, 8d, 8e).

  As shown in FIG. 6A, each check valve structure 8 in the present embodiment is fitted into a valve fixing member 81 disposed on the inner peripheral surface 31 a side of the housing main body 31 and the inflow port portion 55. A valve main body 82 disposed on the rotary shaft 14 side of the rotor 5 with respect to the valve fixing member 81 and a sphere 83 for sealing the combustion gas G are provided. In the description of the configuration of each check valve structure 8 below, the corresponding symbols a, b, c, d, and e are omitted.

  The valve fixing member 81 has a gas passage 811 having a diameter smaller than that of the sphere 83 and is formed in a cylindrical shape, and a screw portion 812 that can be screwed with the inflow port portion 55 is formed on the outer peripheral surface thereof. . The valve fixing member 81 is screwed and arranged on the inner peripheral surface 31a side of the housing main body portion 31 of the inflow port portion 55, one end opens toward the inner peripheral surface 31a side of the housing main body portion 31, and the other end. It opens toward the valve body 82. A ball seat portion 813 for attaching the sphere 83 around the gas passage 811 is formed at the end of the valve fixing member 81 on the valve main body 82 side.

  The valve main body 82 has a gas passage 821 having a larger diameter than the gas passage 811 of the valve fixing member 81 and is formed in a cylindrical shape. The valve main body 82 is fitted and arranged on the pressure gas distribution passage 54 side of the inflow port portion 55. One end of the valve body 82 opens toward the valve fixing member 81, and the other end opens toward the pressure gas distribution passage 54. On the pressure gas distribution passage 54 side of the gas passage 821, as shown in FIGS. 6A and 6B, a tapered portion 822 having a diameter reduced toward the pressure gas distribution passage 54 side is formed. The taper portion 822 has ball seat portions 823 to which the sphere 83 is attached, and four protrusion portions 824 that protrude radially inward of the valve body 82 are formed at equal intervals. The tapered portion 822 is formed so that the combustion gas G can flow in from a portion other than the protruding portion 824 even when the spherical body 83 contacts the spherical seat portion 823.

  As shown in FIG. 6A, the sphere 83 is formed into a true sphere and is disposed so as to be movable in the gas passage 821 of the valve body 82. The spherical body 83 is formed so that the gas passage 811 can be sealed when the spherical body 83 comes into contact with the spherical seat portion 813 of the valve fixing member 81. The spherical body 83 is formed so as to be able to contact with each spherical seat portion 823 of the valve main body 82.

  As shown in FIG. 1, the vane 7 is inserted into a vane groove 51 formed in the rotor 5. Each vane 7 is arrange | positioned so that the hollow part 60 may be divided | segmented into the five chambers 6 (6A, 6B, 6C, 6D, 6E).

  As shown in FIG. 1, the recess 53 of the rotor 5 is formed in each chamber 6 (6A, 6B, 6C, 6D, 6E) to form the recesses 53a, 53b, 53c, 53d, 53e, respectively. To do.

  As shown in FIGS. 3 and 4, each vane 7 is a member in which carbon is impregnated with metal and is formed in a rectangular flat plate shape. In the following description of the configuration of each vane 7, the corresponding symbols a, b, c, d, and e are omitted. As shown in FIG. 3, when viewed from the axial center side of the housing main body 31, sliding surfaces 7m and 7m with the vane groove 51 of the rotor 5 are formed on the surface in the rotation direction, and the side housing portion is formed on the surface in the axial direction. And a sliding surface 7p with the inner peripheral surface 31a of the housing body 31 is formed on the radially outer side, and a pressing surface 7q pressed by the combustion gas G on the radially inner side. Is formed.

  Each sliding surface 7p is formed orthogonal to the radial direction of the rotor 5, as shown in FIG. The sliding surface 7p is formed such that the front corner portion 711 on the rotation direction side of the rotor 5 and the rear corner portion 712 on the opposite side are in sliding contact with the inner peripheral surface 31a. A tip seal groove portion 721 that is recessed toward the rotary shaft 14 of the rotor 5 and into which a vane tip seal 9 to be described later can be fitted is formed in the sliding surface 7 p over the entire axial direction of the rotor 5.

  As shown in FIG. 1, gas passages 72 (72 a, 72 b, 72 c, 72 d, 72 e) through which the combustion gas G flows are communicated with the vane grooves 51 along the radial direction of the rotor 5. ) Is formed.

  In the following description of the configuration of each gas passage 72, the corresponding symbols a, b, c, d, and e are omitted except for some of them. As shown in FIG. 5, each gas passage 72 includes a tip seal groove 721 described above, a large diameter portion 722 opened on the axial center side of the rotor 5, as shown in FIGS. 4 and 5, and as shown in FIG. 5. In addition, a small diameter portion 723 communicating with the tip seal groove portion 721 and a tapered portion 724 formed narrowly from the large diameter portion 722 toward the small diameter portion 723 are provided. As shown in FIG. 4, vents 73 (73 a, 73 b, 73 c, 73 d, 73 e) communicating the gas passage 72 and the vane groove 51 are disposed in the vane 7.

  As shown in FIGS. 3 and 4, the vane tip seal 9 (9a, 9b, 9c, 9d, 9e) is formed in a prismatic shape by a member in which carbon is impregnated with metal, and a gap is formed over the entire tip seal groove portion 721. Is inserted. As shown in FIG. 5, the end portion on the inner peripheral surface 31a side of the vane tip seal 9 has a sliding surface 91 formed in an arc shape protruding toward the inner peripheral surface 31a side.

  As shown in FIG. 1, the housing body 31 includes a fuel injection nozzle 10 for injecting fuel, a valve chamber 4 for switching between inflow of combustion gas G and inflow of low-pressure air, and an ignition plug for igniting the fuel. 12 are arranged.

  As shown in FIG. 1, the fuel injection nozzle 10 is disposed by passing the first build-up portion 31 b in a direction eccentric from the axis of the housing main body 31. An ejection port 10a is arranged in the first build-up portion 31b so that the mixed gas can be ejected from the fuel injection nozzle 10 toward the rotating vane 7. Since the ejected fuel is carried to the near dead center side by the rotating vane 7, when the ignition plug 12 is ignited, the mixed gas is ignited in a compressed state.

  As shown in FIG. 1, the spark plug 12 is disposed by inserting the boss portion 31 d toward the axial center of the housing main body portion 31. An ignition port 12a is arranged in the boss portion 31d so that the ignition plug 12 can ignite the mixed gas mixture gas.

  When the ignition plug 12 is ignited, one of the pair of vanes 7 (the vanes 7 arranged on the rear side in the rotation direction) constituting the chambers 6 when the rotor 5 is rotated reaches the vicinity of the ignition plug 12. It is done at the time.

  As shown in FIG. 1, the valve chamber 4 is formed in the second build-up portion 31c. In the valve chamber 4, a supercharging passage valve (also simply referred to as a valve) 11 is arranged. The valve 11 opens and closes whether or not the air or the combustion gas G in any one of the chambers 6 comes to a position facing a valve inlet 15 described later. In the valve chamber 4, a spring member is opened. 13 is arranged so as to be movable by being urged toward a gas introduction path 20 described later.

  As shown in FIG. 1, a valve inlet 15 that connects the valve chamber 4 and the chamber 6 is formed in the second build-up portion 31 c, and supercharging that is connected to the valve inlet 15 through the valve chamber 4 is performed. An air passage inlet 16 is formed. A supercharged air passage 17 connected to the intake port 18 formed in the side housing portion 32 is connected to the supercharged air passage inlet 16.

  As shown in FIGS. 1 and 2, the intake port 18 is formed so as to communicate with the outside from the side housing portion 32 so as to be able to intake air. An exhaust port 19 communicating from the side housing part 32 to the outside is formed on the rear side of the intake port 18 in the rotation direction of the rotor 5.

  A gas introduction path 20 that connects the chamber 6 and the valve chamber 4 is formed adjacent to the valve inlet 15 on the rear side in the rotation direction of the rotor 5 of the second build-up portion 31c.

  When the combustion gas G in the chamber 6 is introduced into the valve chamber 4 by the gas introduction path 20, the pressure of the combustion gas G overcomes the urging force of the spring member 13 and moves the valve 11 toward the spring member 13. The inlet 15 and the supercharging air passage inlet 16 are closed.

  The intake port 18 and the exhaust port 19 are formed in a long hole shape corresponding to the direction of rotation of the recess 53 formed in the rotor 5. When the concave portion 53 matches the intake port 18, the matched concave portion 53 is connected to the supercharging air passage 17 to become the supercharged air intake opening 21, and when the concave portion 53 matches the exhaust port 19, the matched concave portion 53. Becomes the exhaust opening 22 for releasing the exhaust gas to the outside. In the embodiment, the exhaust port 19 is disposed behind the intake port 18 with respect to the rotation direction of the rotor 5. That is, the concave portion 53 of the rotor 5 is arranged so as to go to the intake port 18 after passing through the exhaust port 19.

  In the engine 1 of the embodiment configured as described above, each stroke is performed by the rotation of the rotor 5 in each chamber 6 divided by the vanes 7 as shown in FIG. In this case, in each chamber 6, an explosion occurs once every two rotations of the rotor 5, during which expansion, exhaust, air intake, air compression, supercharging, scavenging, mixed gas intake, and mixed gas compression are performed. Is called.

  The engine 1 is an improvement of the vane type internal combustion engine disclosed in Japanese Patent Application No. 2006-223338 (Japanese Patent Laid-Open No. 2008-45513), which was previously applied by the present applicant. Since each process of the engine 1 mentioned above is the same also in this invention, detailed description is abbreviate | omitted.

  Next, the operation of the airtight structure 100 will be described. In the state of FIG. 1, the chamber 6A is in an explosion stroke, and the mixed gas that has exploded in the chamber 6A becomes the combustion gas G. As shown in FIG. 4, the inside of the check valve structure 8a provided at the inlet 55a. The combustion gas G flows in. As shown in FIGS. 6A and 6B, the sphere 83 that flows by the combustion gas G contacts the ball seat portion 823 of the protrusion 824 provided on the valve body 82. As shown in FIG. 4, the combustion gas G flows into the pressure gas distribution passage 54 a from a gap portion other than the protrusion 824 of the valve body 82, that is, a portion along the taper portion 822. The combustion gas G that has flowed into the pressure gas distribution passage 54a flows into the adjacent vane groove 51a and also into each pressure gas distribution passage 54 that communicates therewith.

  As shown in FIG. 4, the combustion gas G flowing into the vane groove 51 a hits the pressing surface 7 aq of the vane 7 a, presses the vane 7 a toward the inner peripheral surface 31 a, and flows into the gas passage 72 a in the vane 7 a. The combustion gas G that has flowed into the gas passage 72a flows out from the vent hole 73a into the gap between the sliding surface 7am of the vane 7a and the surface of the vane groove 51a that faces the vane 7a. As shown in FIG. 5, the large diameter portion 722a, the tapered portion 724a, the small diameter portion 723a, and the tip seal groove portion 721a of the vane 7a flow in this order to press the vane tip seal 9a, and the sliding surface 91a is Press against the inner circumferential surface 31a.

  Combustion gas G (indicated by a two-dot chain line arrow in FIG. 6A) that has flowed into each of the other pressure gas distribution passages 54 enters each check valve structure 8 disposed at each inlet 55. As shown by a two-dot chain line in FIG. 6A, the sphere 83 is contacted by the ball seat portion 813 of the valve fixing member 81. When the sphere 83 is in contact with the ball seat portion 813, the combustion gas G is sealed, and the pressures of the pressure gas distribution passages 54, the vane grooves 51, and the gas passages 72 are maintained.

  During the explosion stroke, the volume of the chamber 6 is the smallest, and the pressure in the chamber 6 is maximized by the combustion gas G resulting from the explosion. As the chamber 6 advances from the explosion stroke to the expansion stroke, the volume of the chamber 6 gradually increases. Thus, the pressure in the chamber 6 gradually decreases. The spherical body 83 of the check valve structure 8 into which the combustion gas G is introduced when the pressure in each pressure gas distribution passage 54, each vane groove 51, and each gas passage 72 exceeds the pressure in the chamber 6 is a ball seat portion. 813 is attached. The chamber 6 in the rear stroke of the chamber 6 in which the explosion stroke was performed becomes an air compression stroke, but since the pressure at this time is lower than that in the explosion stroke, each pressure gas distribution passage 54, each vane groove 51, The pressure in each gas passage 72 is maintained until the next explosion stroke.

  Next, the airtight relationship between the combustion gas G generated in the chamber 6 and the vane 7 will be described.

  When the mixed gas inside the chamber 6A is ignited by the spark plug 12 in the state of FIG. 1, the impact pressure of the combustion gas G that has been burned and explosively is applied to the vane 7a, the vane 7e, and the check valve structure 8a. At this time, as shown in FIG. 4, the front corner 711a of the vane 7a located inside the chamber 6A is in line contact with the inner peripheral surface 31a, and the rear corner 712e of the vane 7e is in line contact with the inner peripheral surface 31a. To do. Accordingly, the combustion gas G does not flow into the vane tip seals 9 side, and the vanes 7a and 7e are not pushed into the rotating shaft 14 side of the rotor 5, thereby maintaining the airtightness of the engine 1. it can.

Further, when the stroke advances in FIG. 1 and the rotor 5 rotates in the rotation direction indicated by the arrow, and the combustion gas G is in the region which is the chamber 6E in FIG. 1, as shown in FIG. The front corner portion 711 a of the vane 7 a that moves to the position of the vane 7 e is separated. Therefore, combustion gas G in the region was chamber 6E in FIG. 1, push the vanes 7a and vane tip seal 9 a which is moved to the position of the vane 7e to the rotary shaft 14 of the rotor 5. In this case, the combustion gas G is subjected to as the pressure gas distribution passage 54 in check valve structure 8 a, and each vane groove 51, the pressure applied to the gas passage 72, the same pressure. That is, the force with which the combustion gas G pushes the sliding surface 91 of the vane tip seal 9a from the inner peripheral surface 31a side is equal to the force with which the pushing surface 7q of the vane 7 and the bottom surface of the vane tip seal 9 are pushed.

  In this state, as shown in FIG. 5, the sliding surface 91 and the sliding surface 7p press the inner peripheral surface 31a at the front half portion 711 side half, respectively, so that it is about half of the pressing surface 7q shown in FIG. The pressure of the combustion gas G is received in one area. The pressure ratio is about 1: 2, and the force to press against the inner peripheral surface 31a is superior, so that the airtightness in the chamber 6A is maintained.

  In FIG. 7, the airtightness will be described in detail. Since the force of the combustion gas G applied to the vane 7 is proportional to the projected area, the magnitude and direction of the applied force are schematically indicated by arrows. Assuming that the force of the combustion gas G applied per unit area is one arrow, the force of pushing the vane 7 from the chamber 6 side into the vane groove 51 and the force pushing the vane groove 51 against the inner peripheral surface 31a are compared with each other. Shown in number. In the following description, the gap between the vane groove 51 and the vane 7 and the gap between the vane tip seal 9 and the tip seal groove 721 are emphasized broadly in the drawing. Also, the size of the arrow on the drawing is not proportional to the magnitude of the force. It is assumed that the vane 7 and the vane tip seal 9 have the same thickness. The numbers related to the projected area have been changed to distinguish them from other codes.

  In the vane 7, as shown in FIG. 7, the combustion gas G wraps around the combustion gas G between the sliding surface 91 and the rear corner portion 712 of the vane tip seal 9 a on the rotation rear side of the rotor 5. Absent. Therefore, the vector 23 has two projections because the projection area is 2, the vector 24 has two arrows because the projection area is 2, the total projection area is 4, and the vector 25 is projection for four arrows. Since the area is 6, there are six arrows. As a result, the force to be pressed against the inner peripheral surface 31a becomes larger from the ratio of 2: 3, and the vane 7 can be kept airtight as a partition wall.

  In the vane tip seal 9, the combustion gas G does not enter the sliding surface 91 of the vane tip seal 9 a on the rear side of the rotor 5 on the combustion gas G side. Therefore, the vector 26 has a projection area of 1 and thus the vector 27 has one arrow because the vector 27 has a projection area of 2, and as a result, the force of pressing the inner peripheral surface 31a from the ratio of 1: 2. Therefore, the vane tip seal 9 can be kept airtight as a partition wall.

  In the gap between the vane tip seal 9 and the tip seal groove 721, between the sliding surface 91 and the rear corner portion 712 of the vane tip seal 9a on the rotation rear side of the rotor 5, there is a combustion gas on the combustion gas G side. G doesn't wrap around. Therefore, the vector 28 has two arrows because the projection area is 2, and the arrow 28 on the opposite side. Therefore, by pressing the floating vane tip seal 9 against the end face of the tip seal groove 721, the tip seal groove 721 is pressed. The combustion gas G from 721 does not leak into the adjacent chamber 6.

  The material of the vane 7 and the vane tip seal 9 is made of carbon impregnated with metal. Carbon has self-lubricating properties and heat resistance, and the strength can be increased by impregnating it with metal. By using the same material for the vane 7 and the vane tip seal 9, the coefficient of thermal expansion is the same even when exposed to high temperatures and the lubricity is good, so that the fitting gap can be minimized.

  In the airtight structure 100 of the present embodiment, the combustion gas G generated by the explosion stroke flows into the inlet port 55 located in the chamber 6 where the explosion stroke is performed and the pressure gas distribution passage 54 in this order, and communicates with each other pressure. The gas flows into the gas distribution passages 54 and flows into the vane grooves 51 communicating with the pressure gas distribution passages 54 to press the vanes 7 against the inner peripheral surface 31 a of the housing main body 31.

  Since the vane 7 is pressed against the inner peripheral surface 31a of the housing main body 31 using the combustion gas G generated by the explosion stroke, there is no influence of sag due to heat, and the airtightness of each divided chamber 6 is reduced. Can be held stably.

  In addition, a check valve structure 8 that maintains the pressure in the pressure gas distribution passage 54 and the vane groove 51 by introducing or sealing the combustion gas G is disposed in the inflow port portion 55. Thus, the combustion gas G is taken into the pressure gas distribution passages 54 and the vane grooves 51 during the explosion stroke, and the combustion gas G is sealed in the pressure gas distribution passages 54 and the vane grooves 51 during the other strokes. The airtightness of each divided chamber 6 can be maintained at all times.

  Further, the vane 7 is formed in a rectangular flat plate shape with the sliding surface 7p on the inner peripheral surface 31a side of the housing main body portion 31 orthogonal to the radial direction of the rotor 5, and is located inside the chamber 6 where the explosion stroke is performed. The front corner portion 711 and the rear corner portion 712 are formed so as to be in sliding contact with the inner peripheral surface 31a of the housing main body 31 during the explosion stroke.

  Thereby, the flow of the combustion gas G generated during the explosion stroke is stopped at the front corner portion 711 and the rear corner portion 712 of the vane 7 slidably in contact with the inner peripheral surface 31a of the housing main body portion 31 and exceeds the corner portion 71 of the vane. It is possible to prevent the vane 7 from being pushed into the center of the rotor 5.

  Further, a gas passage 72 that communicates with the vane groove 51 along the radial direction of the rotor 5 and flows in the combustion gas G is formed in the vane 7, and the gas passage 72 on the inner peripheral surface 31 a side of the housing main body 31 is formed. Further, the vane tip seal 9 is fitted, and the sliding surface 91 of the vane tip seal 9 is formed in an arc shape protruding toward the inner peripheral surface 31 a side of the housing body 31.

  As a result, the vane tip seal 9 is pressed against the inner peripheral surface 31a of the housing body 31 by the combustion gas G flowing from the gas passage 72 together with the pressing of the vane 7 itself. Airtightness can be more reliably maintained. Further, since the sliding surface 91 of the vane tip seal 9 is formed in an arc shape, friction with the inner peripheral surface 31a of the housing main body 31 can be reduced, so that the sliding surface 91 of the vane tip seal 9 and the housing main body can be reduced. The sliding contact of the inner peripheral surface 31a of 31 can be made smooth.

  The vane 7 is provided with a vent hole 73 that allows the gas passage 72 and the vane groove 51 to communicate with each other. As a result, the combustion gas G generated by the explosion stroke is caused to flow out into the gap between the vane 7 and the vane groove 51, and the vane 7 is floated by the combustion gas G interposed in the gap, so that the vane 7 and the vane groove 51 Friction can be reduced.

  The check valve structure 8 is inserted into the inlet 55 and communicates with the pressure gas distribution passage 54 so as to allow the combustion gas G to flow therethrough. A valve fixing member 81 disposed on the inner peripheral surface 31a side so as to allow the combustion gas G to flow in or seal, and a sphere 83 housed in a gas passage 821 formed in the valve body 82. It is composed.

  The sphere 83 located in the chamber 6 of the explosion stroke moves to the pressure gas distribution passage 54 side during the explosion stroke to flow G combustion gas into each pressure gas distribution passage 54, and the sphere 83 located in the other region The combustion gas G is sealed by contacting the ball seat 813 of the fixing member 81.

  Thereby, the inflow and sealing of the combustion gas G are switched by the movement of the sphere 83, and the pressure in each pressure gas distribution passage 54 and each vane groove 51 can be maintained, so that the airtightness of each divided chamber 6 is always maintained. Can be held.

  In addition, the vane 7 and the vane tip seal 9 are made of carbon-impregnated metal. By using a carbon member having self-lubricating properties, no lubricating oil is required, so that maintenance can be made free.

  As another embodiment, the vane 7 can be urged toward the inner peripheral surface 31 a of the housing main body 31 by using a spring member as an auxiliary when the engine 1 is started or stopped.

DESCRIPTION OF SYMBOLS 100 Airtight structure 1 Engine 3 Housing 31 Housing main-body part 31a Inner peripheral surface 32 Side housing part 5 Rotor 51 Vane groove 52 Outer peripheral surface 54 Pressure gas distribution channel 55 Inlet part 7 Vane 71 Corner | angular part 711 Front corner | angular part 712 Rear corner | angular part 72 Gas passage 73 Vent hole 8 Check valve structure 81 Valve fixing member 82 Valve member 83 Sphere 9 Vane tip seal 91 Sliding surface G Combustion gas

Claims (5)

A housing, a rotor built in an eccentric manner with respect to the axis of the housing and rotatable in the housing; a plurality of vanes in sliding contact with the inner peripheral surface of the housing; and a plurality of vane grooves in which the vanes slide An air-tight structure of a vane type internal combustion engine comprising:
In the rotor, a plurality of pressure gas distribution passages for introducing high-pressure combustion gas generated by an explosion stroke are disposed,
Each of the pressure gas distribution passages is formed in communication with each other on the axial center side of the rotor, and is formed in communication with each of the vane grooves,
Between the vane grooves on the outer peripheral surface of the rotor, an inflow portion into which the high-pressure combustion gas flows is formed in communication with each of the pressure gas distribution passages.
Each inflow port portion is provided with a check valve structure for maintaining the pressure in the pressure gas distribution passage and the vane groove,
A gas passage is formed in the vane along the radial direction of the rotor, in communication with the vane groove and into which the high-pressure combustion gas flows.
A vane tip seal is inserted into an end of the gas passage on the inner peripheral surface side of the housing,
The tip of the vane tip seal is formed in an arc shape protruding toward the inner peripheral surface of the housing,
The high-pressure combustion gas flows into the pressure gas distribution passages and flows into the vane grooves communicating with the pressure gas distribution passages to press the vanes against the inner peripheral surface of the housing. An airtight structure of a vane type internal combustion engine.   The vane has a rectangular flat plate shape, and an end surface on the inner peripheral surface side of the housing is formed perpendicular to the radial direction of the rotor, and a corner portion located inside an area where the explosion stroke is performed has the corner during the explosion stroke. The airtight structure of a vane type internal combustion engine according to claim 1, wherein the airtight structure is formed so as to be in sliding contact with an inner peripheral surface of the housing. The airtight structure of the vane type internal combustion engine according to claim 1 or 2 , wherein the vane is provided with a vent hole communicating the gas passage and the vane groove. The check valve structure is inserted into the inlet portion and communicates with the pressure gas distribution passage so as to allow the high-pressure combustion gas to flow therethrough, and the inner peripheral surface of the housing from the valve body A valve fixing member disposed on the side and formed so as to be able to flow in or seal the high-pressure combustion gas, and a sphere housed in a gas passage formed in the valve body,
The sphere located in the region where the explosion stroke is performed moves to the pressure gas distribution passage side during the explosion stroke and flows the high-pressure combustion gas into the pressure gas distribution passage, and the sphere located in the other region. the spheres of the check valve is airtight structure of the vane-type internal combustion engine according to claim 1, wherein Te Kisesshi the valve fixing member, characterized in that sealing the combustion gas of the high pressure.   5. The airtight structure of a vane type internal combustion engine according to claim 1, wherein a member in which carbon is impregnated with metal is used for the vane and the vane tip seal. .

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