JPS63140831A - Vane sealing construction for vane pump type rotary piston mechanism - Google Patents

Abstract

PURPOSE:To reduce slide resistance while ensuring sufficient sealing function by forming a groove continuously extending on the edge face of three sections of the outer periphery edges of a vane opposed to the inner surface of a housing and inserting an U-shaped seal plate loosely in the groove. CONSTITUTION:First and second rotary piston mechanisms 300A, 300B in charge of intake, compression and expansion, exhaust strokes rotate respectively rotors 50A, 50B synchronously about ORA in housings 20A, 20B to define respectively operation chambers M with four vanes 80. These vanes 80 are constituted from two coupled plates 84 and formed on edge endface with a groove 83 extending along three sections of the outer periphery. A seal plate 82 longitudinally divided is loosely fitted into the groove 83 at the U-shaped position corresponding to the three sections of the outer periphery of vane 80 and the inner peripheral surfaces of housings 20A, 20B. Thus, the slide resistance is reduced while a high sealing effect can be displayed.

Description

DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to a vane seal structure in a vane pump type rotary piston mechanism, and particularly to a technique useful for a rotary engine using a vane pump type rotating machine.

(Prior Art) A conventional example of using a vane pump type rotary machine in a rotary engine is disclosed in Japanese Patent Application Laid-open No. 5O-112610.

This is achieved by separately providing a rotary piston mechanism that handles the suction and compression strokes and a rotary piston mechanism that handles the expansion and exhaust strokes, and by connecting and combining them.
It is designed to function as a separate internal combustion engine, and uses a vane pump type rotary piston mechanism.

In the rotary piston mechanism of this example, there is only one vane. A single vane passing through the rotor in its diametrical direction is configured as a combination of a plurality of partition plates, and these partition plates are supported in a sliding relationship with each other, and each outer Each partition plate is biased outward so that its peripheral edge is pressed against the inner surface of the housing.

Further, generally known vane pumps have a plurality of vanes arranged radially within a housing so as to rotate together with a rotor, and the outer periphery of each vane is configured to directly slide into contact with the inner surface of the housing.

[Problems to be Solved by the Invention] However, in the former technique, the entire vane moves to maintain airtightness with respect to the housing, so the structure is complicated and the gap between the partition plates that make up the vane is complicated. The problem is that the sliding resistance is extremely large.

However, the latter vane pump has a problem in that sliding resistance is high because the vane tip is directly pressed against the inner surface of the housing to ensure sealing performance.

SUMMARY OF THE INVENTION An object of the present invention is to provide a simple vane seal structure that can reduce the sliding resistance of the vane and exhibit a sufficient sealing function even when used in an internal combustion engine.

[Means for Solving the Problems] The present invention solves the above problems, and includes a rectangular vane that slides its three outer circumferential sides on the inner circumferential surface and both inner surfaces of the housing. By touching and rotating,
In a vane pump type rotary piston mechanism in which the volume of the working chamber increases and decreases, a groove is formed in the end surface of the vane facing the inner surface of the housing on three sides of the outer circumference, and a groove is formed in the groove that extends continuously over the three sides of the outer circumference, and the vane is inserted into the groove. The seal plate is shaped like a U-shape so as to correspond to three sides of the outer periphery of the housing, and is fitted with a seal plate that is separated in the longitudinal direction at a position corresponding to the inner peripheral surface of the housing so as to be freely movable.

In this case, the vane has a structure in which two plates are joined together, a recess is formed on the outer periphery of at least one of the plates on the mating surface side, and the seal plate is secured by the recess. A groove for insertion may be provided.

[Function] In the sole structure of the present invention, since the seal plate is in sliding contact with the inner surface of the housing, wear is absorbed by the sole plate. Further, this seal plate is constructed as a separate member from the vane, and its thickness can be freely selected. Therefore, it can be made as thin as possible, and sliding resistance can be reduced. In particular, if two vanes are used together, an extremely thin sealing plate can be provided. Furthermore, when applied to an internal combustion engine, the internal pressure of the working chamber acts on the back surface of the seal plate, causing the seal plate to function like a piston ring, resulting in a higher sealing effect.

[Actual Example] Hereinafter, one embodiment of the present invention will be explained by taking as an example a case where it is applied to a rotary engine.

The rotary engine in this case is mounted on a motorcycle as shown in FIG. 1, and first an overview of the power unit including the rotary engine will be explained.

FIG. 2 is a front sectional view showing a schematic configuration of the power plant, and FIG. 3 is a sectional view taken along line I-[11 in FIG. 2.

The power unit U is composed of a main rotary engine A, a transmission B, and a clutch C interposed in the power transmission path from the engine A to the transmission B. An AC generator D is connected to the engine A, and an oil pump E and a water pump F are connected to the other rotating shaft of the engine A. And with this,
It constitutes one unit.

Engine A has a structure in which two rotary piston mechanisms 300A and 300B, each of which has a different role, are arranged vertically and combined. Each rotating piston mechanism 300/'1
(300B) is a housing 2OA with a cylindrical inner peripheral surface.
(20B), a rotor 50A (50B) rotatably housed in the housing 20A (20B), and a housing 2 with the proximal end supported by the rotor 50A (50B).
The rotor 5 is disposed radially in the OA (20B), and the tip part slides on the inner peripheral surface of the housing 20AC20B).
It is a vane pump type equipped with four vanes 80 that rotate together with 0A (50B).

In this case, the rotor 50A (50B) is
It has a cylindrical shape with a diameter smaller than the inner circumferential diameter of the OA (20B) by a predetermined dimension.
The housing 20A(
20B). In Fig. 2, OA and OB are the central axes of the inner peripheral surfaces of the housings 2OA and 20B, respectively, and ORA and ORA are the central axes of the inner peripheral surfaces of the rotors 5 and
This is the central axis of 0A and 50B.

Further, the four vanes 80 arranged radially have their base ends attached to a vane support shaft 110 arranged on the central axis 0A (OB) of the housing 20A (20B), and are centered around this vane support shaft 110. and each can be rotated individually.

The vane support shaft +10 is directly supported by the housing 2OA (20B) independently of the rotor 50A (50B), and is inserted from one end into the internal space of the rotor 50A (50B). Each vane 80 has its tip projected to the outside of the rotor 50A (50B) from 1W51 provided on the peripheral wall of the rotor 50A (50B), and uses the point of contact with the inner surface of the groove 5I as a fulcrum.
I3) and is slidable within the groove 51, thereby rotating following the rotation of the rotor 50A (50B). Conversely, by rotating the vane 80, the rotor 50A (50B) follows and rotates.

The rotating piston mechanism 300A has such a structure.

300B operates as follows.

When the rotor 50A (50B) is rotated as shown by arrows A and B in the figure, the inner peripheral surface of the housing 2OA (2 (IB))
The outer peripheral surface of the rotor 50A (50B) and the two vanes 80
．． The working chamber M surrounded by 80 rotates in the same direction. At that time, the rotor 5 (IA (50
B) The distance between the outer peripheral surface and the inner peripheral surface of the housing 20A (20B) is the same as that between the rotor 50A (50B) and the housing 2OA (20B).
B) It becomes minimum when it reaches point P1 where the inner peripheral surfaces are in contact, and becomes maximum when it reaches point P2 180 degrees opposite thereto. In addition, two vanes 80.80 constituting the working chamber M
The opening angle becomes the minimum when the center of the working chamber M reaches the point P, and becomes the maximum when the central part of the working chamber M reaches the point P. Therefore,
The working chamber M has a minimum volume when passing the point P, and P,
The volume gradually expands as it rotates toward P, and reaches its maximum volume when it passes point P, and as it rotates past P, the volume decreases until it reaches point P. Repeat scaling.

Engine A has a rotary piston mechanism 30 configured as described above.
0A and 300B are paired vertically, and the regions where the volume of the working chamber M is minimum are arranged close to each other, and the housings 20A and 120B constituting the two rotary piston mechanisms 300A and 300B are integrally connected ( A communication passage (hereinafter referred to as a "torch hole") 130 is provided at the joining part of the housings 2OA and 20B to communicate the smallest working chambers M of the rotary piston mechanisms 300A and 300B (the integral housing is indicated by 20). It has a configuration that has formed. Then, the upper rotary piston mechanism 300A is made to take charge of the suction/compression stroke, the lower rotary piston mechanism is made to take charge of the expansion/exhaust stroke, and the cylindrical rotary piston mechanism 300A1
300B can be combined to function as one internal combustion engine.

For this purpose, the upper rotary piston mechanism 300A is provided with an intake passage 150, and the lower rotary piston mechanism 300A is provided with an intake passage 150.
B is provided with an ignition plug 160 and an exhaust passage 170. In this case, the upper and lower rotating piston mechanisms 300A, 30
The rotors 50A and 150B of 0B are connected to gears 180 and tSt so that they rotate synchronously in mutually opposite directions (arrow A and direction).
(see Figure 3), and the main boat 151 of the intake passage 150 opens into the area where the volume of the working chamber M expands (the left area in Figure 2), and the exhaust passage +
The main boat 171 of 70 is opened in the region where the volume of the working chamber M is reduced (the right region in FIG. 2), and the ignition plug 160 is opened in the region where the volume of the working chamber M is gradually expanded after passing through the torch hole 130. It is set in the initial area to try.

Further, a sub-boat 152 is further provided below the main boat 151 on the intake side, and a sub-boat 172 is provided above the main boat on the exhaust side.

Because of the above configuration, this engine A operates as follows.

First, the rotor 50A of the first rotating piston mechanism 300A
, the air-fuel mixture is sucked from the intake passage 150 into the working chamber M whose volume is expanded. The sucked air-fuel mixture rotates together with the rotor 50A and the vane 80, and after passing the point P2, is compressed as the volume of the working chamber M is reduced. Then, as it approaches point P1, it is compressed more strongly,
In the maximum compressed state, the mixture flows from the torch hole 130 to the minimum volume working chamber M of the rotary piston mechanism 300B of the rod 2.
Be ejected inside.

The compressed air-fuel mixture discharged into the working chamber M of the second rotary piston mechanism 300B is ignited by the spark plug 160 at an appropriate timing and combusts (explodes), and the expansion energy of the combustion gas pushes the vane 80. , rotates the rotor 50B. Then, the burned gas is carried to the exhaust passage 170 side as the rotor 50B rotates, and is discharged to the outside from the exhaust passage 170 when the working chamber M gradually contracts. By continuously performing the above operations, engine output is obtained from the rotor 50B of the second rotary piston mechanism 300B.

As explained above, in this engine A, housing 2
Gas flows through the inside of 0 along an inverted S-shaped route (see Figure 2),
During this time, the rotor 50 of the second rotary piston machine 1300B follows the suction-compression->ignition-expansion-exhaust process.
Give engine output to B. Therefore, in this engine A, the second rotary piston mechanism 300A
In the figure, the left half is the area responsible for the suction stroke, the right half is the area responsible for the compression stroke, the left half of the second rotating piston mechanism 300B is the area responsible for the expansion (explosion) stroke, and the right half is responsible for the exhaust stroke. It functions as an area for

In addition, in this engine A, the second rotating piston @ structure 3
The rotor 50B of 00B (hereinafter referred to as the second rotor) and the rotor 50A of the first rotating piston mechanism 300A (hereinafter referred to as the first rotor) are connected by gears 180 and 181, and the second rotor 50B is obtained. The rotating horn allows the first
The rotor 50A is rotated. The second rotor 50B is connected to the rear transmission B as the output shaft of the ennon A.

Next, regarding the power transmission system after this output shaft, a rotor shaft 51B is integrally provided as an output shaft in the rotor 50B of the second rotating piston mechanism 300B, and this rotor shaft 51B is connected to the gear 182. .183 to an outer 184 of clutch C, and via clutch C to transmission B. In this case, when the rear side of the second rotating piston mechanism 300B, that is, the side where the intake passage 150 is provided, is the front side of the transmission B, the second rotary piston mechanism 300B is
The rotary piston mechanism 300B is located at the rear of the exhaust stroke area. Note that each axis of the transmission B is parallel to the rotor axis 51B. Further, an AC generator D is connected to the end of the rotor shaft 51B of the second rotary piston mechanism 300B, and an oil pump E and a water pump F are connected to the end of the rotor shaft 51A of the first rotary piston mechanism 300A. has been done.

In this power unit U, the rotational power obtained by the rotor 50B of the second rotary piston mechanism 300B is
The path shown by the arrow in FIG. 3, that is, rotor 50B - rotor shaft 51B - drive gear 182 -> driven gear 18
3→Clutch C→Main shaft 185 of transmission B→Each gear of transmission 14C→Counter shaft 186→Sprocket 187, and is transmitted to the rear wheels, which are driving wheels, by a chain (not shown). Further, the rotation of the second rotor 50B is transmitted to the rotor shaft 51A by gears 180 and +81, and thereby the rotation of the second rotor 50B is transmitted to the rotor shaft 51A.
Apply the necessary power to A to perform suction compression.

Next, how the power unit U having such a structure is mounted on a motorcycle will be briefly described with reference to FIG. 1. In this motorcycle, a loop surrounded by a frame l A power unit U is placed inside.

In this case, the power unit U has the engine A side at the front of the vehicle body,
The transmission B side faces toward the rear of the vehicle body, and the second rotary piston mechanism 300B is located on the lower side, and the first rotary piston mechanism 300A is located above it. The part of the second rotary piston mechanism 300B that is in charge of the expansion stroke is directed toward the front of the vehicle body, so that the traveling wind hits it.

In the illustrated example, an under cowl 2 is provided in front of the second rotary piston mechanism 300B, and the traveling wind rectified from the r-coil guide hole 3 provided in the under cowl 2 flows from the front surface of the second rotary piston mechanism 300B to the lower surface. It's designed to hit the spot.

Further, an intake passage 150 provided in the first rotary piston mechanism 300A extends toward the front of the vehicle body and is connected to the carburetor 4. An air cleaner 5 is installed in front of the carburetor 4, and a radiator 6 is installed in front of it, and the first rotary piston mechanism 300A is hidden behind these devices so that it is not exposed to much wind while driving. ing.

Further, the exhaust passage +70 is connected to the second rotary piston mechanism 30.
It extends diagonally upward from the rear surface of 0B, is curved, and is connected to the exhaust pipe 7.

Furthermore, the ignition plug 160 faces toward the front of the vehicle body like the intake passage 150, and is arranged parallel to the intake passage 150. Further, the main shaft 185 and the counter shaft 186 of the transmission are connected to a second rotary piston mechanism 300.
They are arranged horizontally at approximately the same height as the rotor 50B of B.

Next, referring mainly to FIGS. 4 and 5, the above-mentioned power plant U
Explain the details. For general points, please also refer to FIGS. 2 and 3.

As shown in FIG. 5 (and FIG. 3), the housing 20 constituting the engine A includes a rotary housing 21 on the main body side in which the rotors 50A and 50B are actually housed;
It is divided into a side housing 22 on the lid side. Both housings 21 and 22 are approximately 8-shaped or oval shaped when viewed from the front, and the side housing 22 closes the open side of the rotary housing 21 and is airtightly connected with bolts (not shown). By tightening the housing 20 of the upper and lower two rotating piston mechanisms 300A and 300B.
It consists of

The rotary housing 21 includes two rotary chambers 23A and 23B for forming upper and lower rotating piston mechanisms 300A and 300B.

These rotary chambers 23A and 23B are located in the housing 21
They are opened parallel to each other from one side of the
A partition wall 24 corresponding to the other side housing is formed on the bottom side thereof.

This partition wall 24 is arranged in the width direction of the rotary housing 21,
That is, in FIG. 5, it is provided approximately at the center in the left-right direction, with the left side serving as the main body side casing for forming the engine body, and the right side serving as the bearing casing.

The partition wall 24 has through holes 25A and 25B for passing the rotary shafts 50A and 50B through the rotary chambers 23A and 25B, respectively.
It is provided eccentrically from the center of 23B. In FIGS. 4 and 5, the center of the through hole 25A for forming the upper rotary piston mechanism (first rotary piston mechanism) 300A is shifted downward from the center of the rotary chamber 23A. . Further, the center of the through hole 25B for configuring the lower rotary piston mechanism (second rotary piston mechanism) 300B is the rotary chamber 23B.
It is shifted upward from the center of.

The inner periphery of each through hole 25A, 25B is provided with a cylindrical body portion 26A, 26B extending toward the bearing casing portion, and a mechanical seal 188 and a bearing 189 are fitted and fixed in line on the inner periphery. .

On the other hand, the inner peripheral surface of each rotary chamber 23A, 23B is
The tip of the vane 80 is formed into a highly precise cylindrical surface so that it can slide smoothly, and the rotary chambers 23A, 23
A rotor 50A150B is housed inside B.

The rotor 50A (50B) is cylindrical with a bottom (indicated by reference numeral), and integrally has a rotor shaft 51A (51B) coaxial with the outer periphery of the rotor on the outside of the bottom.

Then, the rotor shaft 51A (51B) is passed through the cylinder body 26A (26B) of the housing 21 and the partition wall 24 is inserted.
The rotor 50A (50B) supports the rotor shaft 51A (51B) with a bearing 188 that extends to the opposite side of the housing 2
0 rotary chamber 23A (23B).

Also, the rotor 50A (50B) is the old tally room 23A.
(23B) has a diameter of about 41B, and by supporting the rotor shaft 51A (51B) as described above, it is inscribed (strictly speaking, in contact) with the cylindrical inner surface of the rotary chamber 23A (23B). (There may be a slight gap that does not interfere with the rotation.)

Note that the upper and lower rotors 50A and 50B are located within the same plane. Further, as shown in FIG. 2, in the upper rotary piston mechanism 300A, the center O of the rotary chamber 23A is
The line LA connecting A and the center ORA of the rotor 50A and the rotary chamber 23 in the lower rotating piston mechanism 300B.
A line L connecting the center OB of B and the center ORB of the rotor 50B
B and B are parallel to each other and slightly shifted from each other. and,
Naturally, the first rotary piston mechanism 3 connected in parallel
Points P, , P, at 00A are on the line LA, and the second
Point 1) 11P in the rotating piston mechanism 300B is on the line LI3.

In this way, each rotary chamber 23A, 2 of the housing 20
Four vane insertion grooves 52 are formed at equal intervals in the circumferential direction on the peripheral wall of the cylindrical portion of the rotors 50A and 50B housed in the rotor 3B. These grooves 52 are formed in the rotor 50A (50B).
) is formed parallel to the axis of the rotor 50A (50B) from the open end side of the rotor 50A.
C50B) in the radial direction.

Four vanes 80 arranged radially are inserted into each WIt52. In this case, the vane 80 is made to be able to freely slide in the direction of the arrow (C) within the groove 52, and also to be able to freely slide in the direction of the arrow (D) using the inner surface of the groove 52 as a fulcrum. ing.

The tip of the vane 80 protrudes from the outer circumference of the row 950A (50B), and the base end inserted into the rotor 50A (50B) is fixed to the vane support shaft 110. This vane support shaft 110 has its base end fixed to the inner surface of the side housing 22, so that the vane support shaft 110 is in a cantilevered state, and the rotor 5
Rotor 50A (50B) so as not to interfere with 0A (50B)
) is inserted into the rotor 50A (50B) from the open end side thereof, and is located on the central axis (OA, Ol in FIG. 2) of each rotary chamber 23A, 23B.

The base end of each vane 80 is attached to the vane support shaft 110 via a bearing holder +11 that can be rotated individually, and the tip is attached to the inner circumferential surface of the rotary chambers 23A, 23B. It is designed to be able to freely rotate around the vane support shaft 110 while making sliding contact. In this case, two mounting pieces 81, 81 are provided at the base end of each vane 80 at an interval, and the vanes 80 are prevented from interfering with each other by the mounting pieces 81, 81. It is fixed to the bearing holder lit.

In addition, the rotors 50A and 50B have vanes 8 as shown above.
0 is set, and a side seal ring 6o is attached to the opening end surface. This side seal ring 6
o has an outer periphery slightly smaller in diameter than the rotor 5oΔ (50B), and is attached to the rotor 50A (50B) by a bolt 61.
B) integrally and concentrically fixed.

On the other hand, the rotor 50A (5
A ring-shaped recess 27 concentric with the center of the side seal ring 6o and a boss 28 projecting from the center of the ring-shaped recess 27 are formed in the side seal ring 6o.
7 and is rotatably fitted to the boss portion 28 via a needle roller 62. As a result, the open end side of the a-tube 50A (50B) is rotatably supported by the side housing 23.

As described above, the rotors 50A, 50 are installed in the housing 20.
By incorporating B, the vane 80, etc., first and second rotary piston mechanisms 300A and 300B, in which the volume of the working chamber M expands and contracts, are constructed.

In this case, the rotor shaft 51A, 5. Gear ratio between IBs is 1:
They are connected by gears +80 and +81, and are configured to rotate synchronously in opposite directions. Here, the first
The rotor 50A of the second rotating piston mechanism 300A is around the cloth in FIG. 4, and the rotor 50 of the second rotating piston mechanism 300B is
B is set to rotate counterclockwise. Therefore, in the first rotary piston mechanism 300A, the left half in FIG. 4 is an enlarged region of the working chamber volume, and the right half is a reduced region, and in the second rotary piston mechanism 300B, the left half is the working chamber volume. The enlarged area and the right half are the reduced area.

Further, the internally rotating piston mechanisms 300A and 300B are formed so that the regions where the volumes of the working chambers M are minimum are close to each other, and the housing 20 is designed to communicate with each other the working chambers M having the minimum volumes. Communication hole (torch hole) 130
is formed.

Further, the first rotary piston mechanism 300A on the upper side is in charge of the suction compression stroke, and the second rotary piston mechanism 300A on the lower side is in charge of the suction compression stroke.
B is set to take charge of the expansion and exhaust stroke.

Therefore, the intake passage 150 is connected to the working chamber volume expansion region of the first rotary piston mechanism 300A, particularly the region where the volume expansion ratio is large, and the second rotary piston mechanism 300A
An ignition plug 160 is provided in the initial region of the working chamber volume expansion of the second rotary piston mechanism 300B, and an exhaust passage 170 is connected to the working chamber volume reduction region of the second rotary piston mechanism 300B.

Next, the torch hole 130, the intake passage 150, the exhaust passage 17
0. How to install the spark plug 160 will be described in detail.

First, the torch hole 130 will be described.

In this engine A, as the rotor 50A of the upper first rotary piston mechanism 300A rotates, the air-fuel mixture is taken in from the intake passage 150 and gradually compressed, and the mixture is gradually compressed from the torch hole 130 to the second rotary piston mechanism 300B.
sent towards. In this case, when the air-fuel mixture is compressed, in the first rotary piston mechanism 300A, the outer periphery of the rotor 50A and the inner periphery of the rotary chamber 23A gradually approach each other, reducing the volume of the working chamber M. It becomes a flat shape. Further, the working chamber M of the second rotary piston mechanism 300B on the side that receives and takes the compressed air-fuel mixture also follows a similar process and has a flat shape. Therefore, the gas is received and transferred between the two flat working chambers.

Therefore, in this engine A, a plurality of (three in the illustrated example) torch holes +30 are arranged at intervals in the axial direction of the rotors 50A and 50B, and the second rotary piston mechanism 300
The air-fuel mixture is uniformly fed into the working chamber M of B.

In addition, the torch hole 130 in this case is connected to the line LA,
LB (see FIG. 3).

In other words, in the first rotary piston mechanism 300A, the torch hole 130 is located in front of the contact point P (in front of the rotor 50A with reference to the rotational direction of the rotor 50A), and in the second rotary piston mechanism 300B, the torch hole 130 is located in front of the contact point P. It is located behind the contact point P (on the rear side with respect to the rotational direction of the rotor 50B).

Therefore, the torch hole 130 is connected to the rotor 50A (50I3).
When viewed in cross section (see Figure 4), it is formed obliquely considering the direction in which gas flows.

That is, when viewed from the first rotary piston mechanism 30OA side, it is directed diagonally downward. In this case, the angle of inclination is preferably set according to the characteristics of engine A, taking into consideration the maximum output and maximum torque of engine A, as will be described later.

Furthermore, these three torch holes 130 are connected to the rotor 50A.
When viewed in a cross section along the axial direction of (50B), they are each oriented in a direction toward the ignition plug 160. In the illustrated example, three torch holes 130 are provided with a circular cross section, but each torch hole 130 may be a long hole. Moreover, it may be a single number or four or more.

Next, the intake passage 150 and the exhaust passage 170 will be described.

As shown in FIG. 4, the intake passage 150 is disposed on the circumferential side of the first rotary piston mechanism 300A, extends toward the front of the vehicle body, and is connected to the carburetor 4. As shown in FIG. 6, the center line of this intake passage 4 is located at a position corresponding to the widthwise center of the rotor 50A, and the intake passage 4 bifurcates in the axial direction of the rotor 50A near the rotary housing 21. The two main boats 151 are connected at right angles to the outer peripheral surface of the rotary chamber 23A, and two main boats 151 are opened on the inner peripheral surface of the rotary chamber 23A.

This main boat 151 is located at the fourth
As shown in the figure, a sub-boat 152 is further provided below the main boat 151, which is a position where the volume of the working chamber M is increased at a large rate. This sub boat 152
is opened on the inner peripheral surface of the rotary chamber 23A near the torch hole 130, and communicates with the intake passage +50 through a narrow auxiliary passage 153. This sub-boat 152 is provided for the purpose of eliminating the negative pressure that occurs at the beginning of the process of expanding the volume of the working chamber M, so from the point of view of eliminating the negative pressure, it is sufficient to provide one, but it actively increases the air-fuel mixture. If it is desired to avoid promoting air intake, a plurality of them may be provided.

Further, the exhaust passage 170 is connected to the second rotary piston mechanism 30.
It is arranged on the side in the circumferential direction of 0B and is directed diagonally upward to the rear of the vehicle body. This exhaust passage 170 has a slightly smaller diameter than the intake passage 150, as shown in FIG.
50, the center line is located at the center in the width direction of the rotor 50B, and is connected at right angles to the outer circumferential surface of the rotary housing 21, with a main boat 171 opening at the inner circumferential surface of the rotary chamber 23B.

In this case, as shown in FIG.
The main bow 1-171 extends upward from the right shoulder of the rotary piston mechanism 300B, but the main bow 1-171 is widened toward the bottom of the rotary chamber 23B. Therefore, as soon as the working chamber M starts to reduce its volume, the main boat 171
The starting end of the exhaust gas passage 170 is opened, and the expanded gas runs toward the exhaust passage 170.

Furthermore, a sub-boat 172 having an extremely small opening area compared to the main boat 171 is provided above the main boat 171 . This sub-boat 172 is opened on the inner peripheral surface of the rotary chamber 23B near the torch hole 130, and has an auxiliary passage 1 narrower than the exhaust passage 170.
73 for communication. Note that the exhaust passage 170 and the auxiliary passage 173 may also be bifurcated like the intake side.

Next, let's talk about the ignition plug.

The ignition plug 160 is located in front of the torch hole 130, that is, in the second
It is arranged in front of the rotor 50B in the rotational direction, and faces the air-fuel mixture flowing in from the torch hole 130. In this case, the electrode 161 is connected to the rotary chamber 2
It is arranged in a recess 29 formed in the inner circumferential surface of 3B. Although a part of the lower side (front side in the rotational direction of the rotor 50B) of this recess 29 is open toward the inside of the rotary chamber 23B, most of the upper part is closed to the rotary chamber 23B by the small partition wall 30.
It is separated from 3B. In other words, the electrode 161 is hidden behind the small partition wall 30. The air-fuel mixture introduced from the torch hole 130 is prevented from directly hitting the electrode +61.

In this embodiment, one spark plug 160 is provided at a position corresponding to the widthwise center of the rotor 50B. and,
A flame nucleus is formed in the widthwise center of the working chamber M,
As the volume of the flame increases, the flame spreads smoothly to the surrounding area.

Note that a plurality of spark plugs 160 may be arranged in the axial direction of the rotor 50B. In this case, the torch hole 13
It is best to point 0 at each spark plug. Also, when viewed from the outside, is the spark plug 160 located below the intake passage 150 extending toward the front of the vehicle?
0 is oriented substantially parallel to the intake passage 150 to facilitate maintenance and inspection.

The main components of engine A have been described above, and next, various seal systems, lubrication systems, and cooling water systems will be explained.

First, let's talk about the seal system.

In each rotating piston mechanism 300A (300B),
Swing portion sealing devices 220 and 240 are provided between the vane 80 and the vane insertion groove 52 to smoothen sliding and swinging of the vane 80. Compression side rotating piston mechanism 300A and expansion side rotating piston mechanism 300B
The two are provided with sealing devices having different structures; the former sealing device 220 is shown in FIG. 8, and the rear sealing device 240 is shown in FIG. 9.

In the sealing device 220 of the compression-side rotary piston mechanism 300A shown in FIG. 8, first, the inner and outer circumferential ends 221 of the vane insertion groove 52 on the rotor 50A side are opened in a V-shape with a predetermined opening angle. . In addition, seal member insertion grooves 222 are formed on both inner surfaces of this @52 so as to be located midway in the depth direction (radial direction of the rotor 50A) of the spacer groove 52 and to face each other. This seal member insertion groove 222 is formed parallel to the axis of the rotor 50A.
The cross section is almost rectangular.

A piano wire-shaped sealing member 223 with a circular cross section is inserted into the insertion groove 222 so as to be slidable in the depth direction of the gap 222.
2. A spring 224 inserted into the bottom part is always biased in the direction of protruding from the groove. Therefore, both seal members 223 are in a relationship where the distance between them is narrowed, and the tip of the seal member 223 comes into pressure contact with the side surface of the vane 8o, thereby reducing the gap between the vane 80 and the vane insertion groove 52.
Sealing is achieved regardless of sliding and swinging of the vane 80.

In this case, since the vane 8o swings about the seal member 223 as a fulcrum, the seal member 223 also functions as a vane support member.

On the other hand, in the expansion side rotating piston mechanism 300B,
Sealing device 240 with higher sealing performance and stronger resistance to pressure
is used. As shown in FIG. 9, in this sealing device 240, first, the outer end of the vane insertion groove 52 on the rotor 50B side, that is, the opening edge 241 on the radially outer side of the rotor 50B has a predetermined opening angle. holding it open. In addition, semicircular grooves 242 are provided in the middle of the vane insertion groove 52 in the depth direction on both inner surfaces of the vane insertion groove 52 to face each other. This semicircular groove 242 connects a hole with a diameter larger than the width of the vane insertion groove 52 from the end of the rotor 50B to the rotor 50B.
It is formed by opening parallel to the axis of 0B.

A semicircular swinging member 243 formed to match the shape of the WIt 242 is fitted into these semicircular grooves 242 so as to be able to swing freely in the circumferential direction. The vane 80 is sandwiched by the vane sandwiching surfaces 244 of the two seed moving members 243, 243, and is supported slidably in the plane direction of the swingable vane.

The vane sandwiching surface 244 of the swinging member 243 functions as a sliding surface for the vane 80, and this surface 244
The seal member insertion groove 24 runs in the axial direction of the member 243.
5 are formed in parallel at intervals. In this seal member insertion M 245 i:, a metal seal plate 246 made of the same material as the piston ring is inserted so as to be slidable in the direction of protrusion and retraction, and a spring 247 housed in the bottom of the groove 245 always keeps the groove 245 It is urged in the direction of going outside, and its tip is pressed against the side surface of the vane 80.

Further, the outer circumferential arcuate surface 248 of the semicircular swinging member 243 is
This is a sliding surface with the inner surface of the semicircular groove 242 on the rotor 50B side, and an oil groove 249 for supplying oil is provided along the axial direction here. These oil grooves 249 are communicated with the vane sandwiching surface 244 side through small through holes 250, and the oil flowing along the surface of the vane 8° reaches the outer circumferential arcuate surface 248 from the small through holes 250, and slides. It is designed to provide surface lubrication.

Next, the sole of the outer periphery of the vane 80 will be explained.

Since each vane 80 slides at high speed on the inner surface of the rotary chamber 23A (23B), the sliding portion is provided with a seal as shown in Fig. 1θ in order to absorb wear and maintain good sealing performance. A seal plate 82 is provided.

Here, the vane 80 has a rectangular shape, and its outer circumference 3
The sides are in sliding contact with the inner peripheral surface and both inner surfaces of the rotary chamber 23A (23B). Therefore, seal plates 82 are embedded in the end faces of these three outer periphery sides. In this case, a groove 83 is formed in the outer peripheral end surface of the vane 80 and extends continuously over three sides of the outer periphery, and a seal plate is formed in the groove 83 in a mouth shape to correspond to the three sides of the outer periphery of the vane 80. 82 is inserted. And the seal plate 82
is held movable within the groove 83 like a piston ring.

By the way, this seal plate 82 is attached to the rotary chamber 2.
Since it slides at high speed on the inner surface of 3A (23B), it is preferable to make it as thin as possible in order to reduce the sliding resistance. However, it is very difficult to form an extremely narrow groove 83 on the end face of the vane 80. Therefore, here, as shown in FIG. 1t, the vanes 80 are made into a two-layered structure to form the narrow grooves 83. That is, recessed portions 85.85 are formed on the outer periphery of the mating surfaces of each plate 84.84, and by bringing both plates 84.84 together, the groove 83 is formed by these recessed portions 85.85. There is. In this way, no matter how thin the groove is, it is possible to manufacture it.

Then, an extremely thin seal plate 82 is inserted into the groove 83 configured in this way. This seal plate 82
may be a cast product or a steel forging.

Further, in this case, the seal plate 82 is divided into two at the center corresponding to the outer periphery of the vane 80, and
It is now possible to move not only outward in the radial direction of A (5oB) but also to the side.

Further, the divided portion of the seal plate 82 has an overlapping structure as shown in FIG. 12 or 13, so that gas leakage does not occur in the front and back directions of the seal plate 82, that is, in the direction of movement between adjacent working chambers. There is no such thing.

It should be noted that such a seal structure is subject to load movement, especially in the case of the expansion-side rotary piston mechanism 300A, which is subject to high temperature and high pressure conditions. For this reason, this seal structure is employed at least in the rotation piston mechanism 300A on the expansion side.

Although the rotation piston mechanism 300B on the compression side is employed in this embodiment, it does not necessarily need to be employed.

In addition, when the vane has a two-piece construction, as shown in FIG.
1, a portion 111a of the vane holder 111 may be integrally formed in a semicircular shape.

Furthermore, in addition to the combination of two sheets, it is also possible to configure a combination of three sheets. In that case, the groove 83 can be created on the outer periphery of the vane 80 by simply retracting the three outer periphery sides of the middle plate a little inward.

In addition, the sole plate 82, as shown in FIG.
It may be divided at the edge of the central side. It is sufficient to finish the vane in any way and to divide it so that it can be displaced in three directions (E, H, and G directions): the outer circumferential direction of the vane and both sides.

Next, the seal on the side surface of the rotor 50A (50B) will be described.

As shown in FIG. 5, on the side surface of the rotor 50A (50B), the aforementioned side seal ring 60 is provided on the left side in the figure, and another side seal ring 70 is provided on the right side.

The right side seal ring 70 is attached to the rotor sleeve 5IA (5
1B) to rotate together with the rotor 50A (50B), and the aforementioned mechanical seal 188 is in sliding contact with the outer periphery of the boss portion 71. This side seal ring 70 is connected to the housing 20 and the rotor 50A.
(50B), and is housed in a side seal ring storage space 31 formed in the housing 20. A labyrinth 72 is formed around at least one circumference of the side seal ring 70 and is configured to exhibit a labyrinth effect with the inner periphery of the storage space 31 to seal the side surface of the working chamber.

Further, a side seal plate 73 is sandwiched between the side surface of the rotor 50A (50B) and the side seal ring 70, and this side seal plate 73 allows the rotor 50A (
50B) and the inner surface of the housing 20. This seal plate 73 is made by stacking several plates.

Furthermore, the other left side seal is configured in almost the same way as the right side seal. That is, the side seal ring 60 is housed in the ring-shaped recess 29 of the side housing 22, and a labyrinth effect is created between the inner periphery of the recess 29 and the outer periphery of the side seal ring 60. Furthermore, a gap between the side surface of the rotor 50A (50B) and the inner surface of the housing 20 is sealed by the side seal plate 61 sandwiched between the side seal ring 60 and the side surface of the roller 50A (50B).

Next, a system for supplying lubricating oil to the several sliding parts mentioned above will be described.

As shown in FIG. 5, the vane support shaft 11O is fixed in a cantilevered manner by tightly fitting into a hole 32 formed in the side housing 22, so that the shaft end surface 112 is exposed to the outside. ing. Inside the vane support shaft 110, there is an oil hole 113 through which lubricating oil is introduced from the shaft end surface 112.
is formed so that oil can first be supplied to the needle roller 114 in the bearing holder Ill that supports the vane 80.

The lubricating oil supplied to the needle roller 114 is scattered by centrifugal force and adheres to the inner circumferential surface of the rotor 50A (50B), and then enters the vane insertion groove 52 and enters the aforementioned swing portion sealing device 220. 240 and then vane 8
0 to the seal plate 82 at the tip of the vane 80, which lubricates the sliding part and also seals the rotor 50A (50
It goes around the side of B) and lubricates the side seal part.

Since each sliding portion is thus configured to be lubricated, not only the wear of the sliding portions is reduced, but also losses such as rotational resistance are reduced.

In addition, regarding other points of this engine A, as shown in FIGS. 4 and 5, passages 35 for passing cooling water are formed in necessary locations of the □ housing 20. Furthermore, a recess 55 is provided on the outer peripheral surface of the rotor 50A (50B), as shown in FIG. 5, so that the air-fuel mixture flows smoothly. Further, since the second rotary piston mechanism 300B side is exposed to harsher conditions, the rotor shafts 51A, 51B, vane support shaft 110, etc.
A stronger one, that is, a thicker one, is adopted than that of the rotary piston mechanism 300A.

Next, parts such as the transmission B1 clutch C will be explained.

As shown in FIG. 4, the transmission B is arranged on the rear side of the second rotary piston mechanism 300B.

The casing 200 of the transmission B is made as an integral structure with the rotary housing 21 on the engine A side, and as shown in FIG. 5 (or FIG. is set to . The position of the split plane is indicated by arrows X and Y.

The left split surface X is a mating surface between the rotary housing 21 and the side housing 22.

In addition, each shaft on the transmission side B, that is, the main shaft 18
5 and the counter shaft 186 etc. are the rotor shaft 51A,
It is arranged parallel to 51B, making it easier to improve the accuracy of machining the shaft holes.

Similarly to the engine A, the transmission is also configured such that it can be assembled by inserting the shaft, gears, etc. into the casing 200 from the left side in the figure. 2 in the diagram
01 is a lid, and this lid 201 is constructed integrally with the side housing 22, and can be fixed to the transmission casing 200 at the same time as fixing the side housing 22 on the engine A side.

In this way, since the casing 200 and M2O1 are each integrated with the housing parts of the engine A,
Machining the split surface becomes easier and at the same time improves machining accuracy.
Furthermore, duplication of tightening screws is avoided, improving ease of assembly.

Further, on the right side of this transmission B in FIG. 5, a clutch C is arranged. This clutch C has clutch inner 1
90 is connected to the main shaft 185, and the clutch outer 184 is connected to the rotor shaft 51B of the second rotary piston mechanism 300B via a pair of gears 182 and 183°. Further, by moving the operating rod 191, the connecting/disconnecting operation can be performed. In this case, the rod 191 is operated by hydraulic pressure, and the rod 191 passes through the inside of the main shaft 185 and is guided to the outside. 192 is a piston device for operating the rod.

In addition, the mouth/end shaft 5 of the second rotary piston mechanism 300B
At the end of 113, an AC generator D is provided,
As described above, the oil pump E and the water pump F are connected to the ends of the rod shaft 51B of the first rotary piston mechanism 300A. These clutches C5, AC generator D1, oil pump E1, and water pump F, which are arranged on the right side of engine A, are all connected to the housing 20.200 on the engine A side and the transmission B side by a splitter Y in an integrated casing. It is wrapped by 201.

Next, the operation of the power plant as described above will be explained.

In the engine A, as previously explained in the overview, the rotor 50A of the first rotary piston mechanism 300A rotates to suck the air-fuel mixture from the intake passage 150 into the working chamber M whose volume is expanded. . in this case,
Since the main boat 151 is at a large portion of the expansion rate of the working chamber volume, the air-fuel mixture can be efficiently filled into the working chamber M.

By the way, in this first rotating piston mechanism 300A, as shown in FIG.
0 and the main bow 1-151 of the intake passage 150, there exists a region where the volume of the working chamber M increases, although it is small. Therefore, if this area is blocked, negative pressure will be generated within the working chamber M as the rotor 50A rotates.

When negative pressure is generated, a rotational force is applied to the vane 80 and the rotor 50A in the opposite direction to the normal rotation direction, which acts as an obstacle to the rotation of the rotors 50 and A and causes a decrease in mechanical efficiency. Become.

However, in the engine A of the embodiment, since the sub-boat 152 is opened to the area where negative pressure is generated, the generation of negative pressure is almost eliminated and mechanical efficiency is improved.

Moreover, since this sub-boat 152 is provided, fresh air can be immediately sucked in when the compressed air-fuel mixture is sent to the second rotary piston mechanism 300B side.

Furthermore, by taking in air from the sub-boat 152, continuity is given to the intake operation, and the inertia of the air-fuel mixture passing through the intake passage 150 can be fully utilized. Therefore, the filling efficiency is increased, contributing to improved output.

In addition, the vane 80 and the circumferential portion of the rotor 50A that have passed through the torch hole 130, and the housing 2 around the torch hole 130
0, the temperature is high due to the influence of twisting heat on the second rotary piston mechanism 300B side.

In this embodiment, since the intake sub-boat 152 is located in the high-temperature part, it is introduced into the working chamber M. These high-temperature parts are cooled by the air-fuel mixture.

On the other hand, the air-fuel mixture has the advantage of being warmed by receiving heat. Also, from the point of view of heating the air-fuel mixture, the working chamber M
Since the conveyance length of the air-fuel mixture sent to
By the time it is discharged toward 00B, it is sufficiently heated and atomization is promoted.

Furthermore, the influence of intake pulsation is reduced by the pulsations occurring on the main boat 151 side and the pulsations occurring on the sub boat 152 canceling each other out.

The air-fuel mixture sucked into the working chamber M as described above is
It rotates and is compressed together with the rotor 50A and the vane 80. Then, in the maximum compressed state, it is discharged from the torch hole 130 into the minimum volume working chamber M of the second rotary piston mechanism 300B.

At this time, since the torch hole 130 is oriented obliquely so as to follow the flow direction of the air-fuel mixture as much as possible, the compressed air-fuel mixture is not subjected to much flow resistance and is moved to the second rotary piston mechanism 3.
Get blown out to the 00B side.

Further, since the torch hole 130 is oriented toward the ignition 1160, the air-fuel mixture enters toward the ignition plug 160 and is dispersed at the same time.

The compressed air-fuel mixture thus discharged into the working chamber M of the second rotary piston mechanism 300B is ignited by the spark plug 160 at an appropriate timing, combusts (explodes), and expands as the combustion progresses. In this case, the electrode 16 of the spark plug 160
1 is located in a recess 29 formed on the inner periphery of the rotary chamber 23B, and is separated by a small partition 30 so that the air-fuel mixture is not blown directly onto the rotary chamber 23B. Therefore, stable ignition is performed without causing the so-called fogging phenomenon. . And this electric 4
The ignition spark from 4161 serves as a nucleus and a flame propagates through the air-fuel mixture in the working chamber M, causing a sudden increase in gas pressure to push the vane 80 and rotate the vane 80 and the rotor 50B. At this time, the vanes 80 are perpendicular to the flow of combustion gas, and the peripheral surface of the rotor 50B is in a relationship along the same flow. For this reason,
The gas pressure is effectively converted into the rotational force of the vane 80, that is, the rotational force of the rotor 50B.

The burned gas is then carried to the exhaust passage 170 side as the rotor 50B rotates, and is discharged from the main boat 171 to the exhaust passage 170 when the working chamber M gradually contracts. By performing the above operations continuously, the rotor 5 of the second rotary piston mechanism 300B
Engine output is obtained at 0B. Part of this output is
It is used to drive the rotor 50A of the rotating piston mechanism 300A.

Note that it is difficult to open the main boat 171 of the exhaust passage 170 largely near the torch hole 130 due to layout constraints. Therefore, there is a region between the main boat 171 and the torch hole 130 where the volume decreases after exhaustion. Therefore, if this region is blocked, the gas remaining in the working chamber M without being discharged will be further compressed, and the efficiency will be reduced by this compression energy. Furthermore, if the remaining gas is compressed and a new compressed air-fuel mixture is received, the filling efficiency may deteriorate.

However, in this embodiment, the sub-boat 172 is provided to prevent as much gas from remaining as possible, so that almost no loss occurs due to compression. Furthermore, since almost no unnecessary gas remains, the filling efficiency in the next cycle is improved. Therefore, together with the function of the sub-boat 172 on the intake side described above, this greatly contributes to improving mechanical efficiency.

The main operations of engine A have been described above, and next, the operation of the seal system of engine A will be explained.

As shown in FIG. 8, the swing part sealing device 220 between the vane 80 and the rotor 50A used in the first rotary piston machine 11300A has a sealing member 223 in pressure contact with the side surface of the vane 80 at all times. This pressure contact surface seals. Thus, the sealing performance of the working chamber M is ensured. This sole device 220 portion includes a rotor 50
Since the lubricating oil supplied into A is automatically flowed in by centrifugal force, the durability and sealing performance of the sliding parts are maintained over a long period of time.

Further, the lubricating oil passes through the vane 80 from the vane insertion groove 52 and reaches the sliding portion at the tip of the vane 80, thereby lubricating this portion. Therefore, the sliding resistance in this part is reduced, providing advantages in terms of mechanical efficiency and durability.

Also, a swinging portion sealing device 24 between the vane 80 and the rotor 50B used in the second rotating piston mechanism 300B
0, as shown in FIG. 9, the seal plate 246 is constantly pressed against the side surface of the vane 80 in two stages.
At the same time, the reaction force presses the swinging member 243 against the inner surface of the semicircular groove 243. These pressure contact surfaces seal the inside and outside of the rotor, thereby ensuring the sealing performance of the working chamber M.

This sealing device 240 is a rotary piston mechanism 3 on the compression side.
Although it is used under harsher conditions (high temperature, high pressure) than 00A, the swinging part and sliding part are separated to improve mechanical reliability, so the sealing performance in this part will last for a long time. A high f-niri is secured. Similarly to the first rotary piston mechanism 300A described above, the lubricating oil supplied into the rotor 50B is automatically supplied to this sealing device 240 portion by centrifugal force. In this case, since the clamping surface 244 side of the swinging member 243 and the arcuate surface 248 are communicated through the oil guide hole 250, lubricating oil is always supplied to these sliding parts.

Next, a seal plate 8 provided at the outer peripheral end of the vane 80
The effect of 2 will be explained.

The seal plate 82 is movable in a groove 83 at the tip of the vane 80, and is moved outward by centrifugal force and spring force (if a spring (not shown) is inserted into the bottom of the seal plate). It is pressed against the inner surface of the rotary chamber 50A (50B). Therefore, the hermeticity of the working chamber M is ensured.

Furthermore, in the case of the second rotary piston mechanism 300B, the pressure of combustion gas acts on the back surface of the seal plate 82, so the seal plate 82 is displaced outward and the housing 2
It is crimped onto the inner circumferential surface of 0 and performs a sealing function like a piston ring. Therefore, the vane 80 and the inner surface of the rotary chamber 23A (23B) are well sealed, and the sealing performance of the working chamber M is maintained more tightly.

Also, by providing the seal plate 82, which is a separate member, at the tip of the vane 80, the rotary chamber 2
The seal plate 82 absorbs all the wear between the vane 3A (23B) and the vane 80. In this case, since the seal plate 82 is made of an extremely thin material, the sliding resistance is small, which greatly contributes to improving mechanical efficiency.

As mentioned above, in this engine A, the housing 2
Gas flows through the inside of 0 along an inverted S-shaped route (see Figure 2),
During this period, the rotor 50 of the second rotary piston mechanism 300B follows a process of suction, compression, ignition, expansion, and exhaust.
Give engine output to B. This rotational output is then transmitted to the drive wheels via the clutch C1 transmission B.

Note that the present invention can of course be applied to rotary engines other than the rotary engine having the above-mentioned configuration as long as they use vanes.

Further, the present invention is also applicable to rotating piston mechanisms other than rotary engines.

[Effects of the Invention] As explained above, the present invention has a structure in which grooves are formed on three sides of the outer periphery of the vane, a seal plate is fitted into the grooves in a freely movable manner, and the sole plate is brought into sliding contact with the inner surface of the housing. Therefore, all wear is absorbed by the seal plate.

In addition, this seal plate is constructed as a separate member from the vane, and the thickness can be freely selected.
It can be made as thin as possible to reduce sliding resistance. Especially when two vanes are combined,
Since an extremely thin seal plate can be provided, sliding resistance can be significantly reduced.

Furthermore, when applied to an internal combustion engine, the internal pressure of the working chamber acts on the back surface of the sole plate, and the seal plate functions like a piston ring, resulting in a higher sealing effect.

Moreover, this seal structure is simply a structure in which a groove is formed on the outer circumferential end surface of the vane and a seal plate is inserted into the groove, and the structure is extremely simple and easy to implement.

[Brief explanation of the drawing]

FIG. 1 is a side view of a motorcycle equipped with a rotary engine to which an embodiment of the present invention is applied, and FIG. 2 is a side sectional view showing a schematic configuration of a power unit including the rotary engine.
Figure 3 is a sectional view taken along line I-III in Figure 2, Figure 4 is a front sectional view showing details of the power unit, and Figure 5 is a cross-sectional view of Figure 4.
-■ line sectional view, Figure 6 is a view taken along the ■-■ arrow in Figure 5, Figure 7 is a view taken along the ■-■ arrow, Figure 8 is a detailed view of the inside of S in Figure 4, and Figure 9 is a view taken along the ■-■ arrow in Figure 5. FIG. 4 is a detailed view of the inside of T, FIG. 10 is a sectional view of the vane tip shown as an embodiment of the present invention, FIG. 11 is an exploded structural view of the same vane, and FIGS. 14 is a diagram showing an example of a temporary pond as a vane half shown in FIG. 11, and FIG. The figure shows an example. A...Engine 300A...First rotating piston mechanism 300B
...Second rotating piston mechanism 20.20 A,
20 B...Housing 21...Rotary housing 22...Side housing 23A, 2.3B...Rotary chamber 50A, 5
0B... Rotor 51A, 51B... Rotor shaft 80... Vane 82... Seal plate 83... Groove 84...・Plate 85 as a vane half...
・Concave part. Applicant: Honda Motor Co., Ltd. Figure 8 Figure 9 Figure 1 Theta 1000 ~

Claims (2)

[Claims] (1) In a vane pump type rotary piston mechanism in which the volume of the working chamber increases and decreases by rotating a rectangular vane with its three outer circumferential sides in sliding contact with the inner circumferential surface and both inner surfaces of the housing, respectively, A groove extending continuously over the three outer circumferential sides is formed on the end face facing the inner surface of the housing on three outer circumferential sides of the vane, and the groove is shaped in a U-shape to correspond to the three outer circumferential sides of the vane, and A vane seal structure in a vane pump type rotary piston mechanism, characterized in that a seal plate divided in the longitudinal direction at a position corresponding to the inner peripheral surface of the housing is fitted in a freely movable manner. (2) The vane has a structure of two plates put together,
A vane sealing structure in a vane pump type rotary piston mechanism according to claim 1, wherein the groove is constituted by a recess formed in an outer peripheral portion of at least one of the plates on the mating surface side. .