JPH11255197A - Sealing system for rotary vane type steering engine - Google Patents

Abstract

PROBLEM TO BE SOLVED: To eliminate damage of a ringlike sealing material interposed between a casing end face inner surface of a rotary vane type steering engine and a rotor end face so as to enhance sealing reliability for the sealing material. SOLUTION: In a rotary vane type steering engine, a ringlike sealing material 12 for sealing a clearance between an inner face of a casing end face 1A and an end face 3A of a rotor 3 is a ringlike base body 12A of smaller diameter than a circumference of an edge 3B of a rotor end face 3A, and is formed into a form having integrally a diameter-directionally projected part 12B in an outer circumferential position corresponding to a fixed segment 4, and a longitudinal sealing material 9 for sealing a clearance between the fixed segment 4 and the rotor 3 is brought into pressure contact with the projected part 12B of the sealing material 12. A lateral sealing material 13 for sealing a clearance between the inner face of the casing end face 1A and the end face of a vane 5 is extended upto a position contacting with an outside diameter of the sealing material 12 from the base part of the vane 5 toward an inside-diametric direction in the rotor 3 to be brought into pressure contact with the sealing material 12.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a seal system for a rotary vane type steering gear.

[0002]

2. Description of the Related Art As a steering machine, FIG.
2. Description of the Related Art A rotary vane-type steering machine as shown in FIG.

In this rotary vane type steering machine, a cylindrical rotor 3 is coaxially supported in a cylindrical casing 2 whose end face is closed by a casing cover 1A and a casing bottom face 1B (see FIG. 12). The space between the inner surface of the rotor 2 and the outer surface of the rotor 3 is circumferentially divided by a plurality of fixed segments 4... 4 and a plurality of vanes 5. … 6
Is controlled so as to generate a rotational torque around the axis of the rotor 3.

The fixed segments 4 project from the inner surface of the casing 2 and come into contact with the outer surface of the rotor 3, and the vanes 5 project from the outer surface of the rotor 3 and come into contact with the inner surface of the casing 2. .

In FIG. 1, reference numeral 6A denotes an oil port of the oil chamber 6, and the oil pressure of the oil chamber 6 is controlled by oil press-fitted or discharged from the oil port 6A. 2A is the casing cover 1A and the casing 2
4 shows a storage groove for an oil ring for sealing between the oil ring and the oil ring.

[0006]

In this rotary vane type steering device, torque is generated by utilizing a hydraulic pressure difference between adjacent oil chambers 6, 6, so that a fixed portion (casing) forming the oil chambers 6, 6 is formed. Cover 1A,
It is necessary to ensure the seal between the contact surface between the inner surface of the casing 2, the bottom surface 1B of the casing, the fixed segment 4) and the movable portion (the rotor 3, the vane 5) and the seal between the fixed seal and the movable seal.

In a conventional rotary vane type steering gear seal system, a casing cover 1A and a casing bottom 1B are provided.
(Since the seal structure of this end face is only vertically symmetrical and the actual seal structure is the same, only the casing cover 1A side will be described below.) The seal between the rotor end face 3A and FIG. As shown in FIG. 13 showing a partial cross-sectional view taken along the line EE of FIG. 13, a ring-shaped sealing material 7 having a diameter slightly larger than the outer diameter of
A and the end face 3A of the rotor were pressed and inserted.

Reference numeral 1C denotes a groove for accommodating the ring-shaped sealing member 7 provided in the casing cover 1A. The seal between the fixed segment 4 and the rotor 3 is formed by a vertical sealing material 9 disposed along the fixed segment 4 as shown in FIG.
And seal the end corner 9A of the vertical sealing material 9 with F
As shown in FIG. 14, which shows a partial cross-sectional view of the portion, the outer peripheral corner 7A of the ring-shaped sealing material 7 is pressure-bonded in an overlapping manner to prevent oil leakage from a contact portion between the sealing materials.

A seal between the vane 5 and the inner surface of the casing cover 1A is provided by a lateral seal member 10 provided on an end surface of the vane 5, and a gap between the vane 5 and the ring-shaped seal member 7 is shown in FIG.
As shown in FIG. 15, which shows a partial cross-sectional view of a portion G of FIG.
A pressure was applied to A in an overlapping manner to prevent oil leakage between the seal materials.

The space between the vane 5 and the inner surface of the casing 2 is sealed by a vertical vane seal 9B. 9C is an oil chamber formed on the back surface of the vertical sealing members 9 and 9B. The oil chamber 9C has a balance hole 11 shown in FIGS.
The hydraulic pressure is guided from the oil chamber 6 through the hydraulic pressure path 11A, and the vertical sealing members 9 and 9B are pressed against the outer peripheral surface of the rotor 3 or the inner surface of the casing 2 by the hydraulic pressure.

The balance hole 11 is a valve for introducing oil pressure from the oil chamber 6 on the high oil pressure side to the oil pressure path 11A. As shown in the sectional view of FIG. Communication hole 1 opening to 6
10 are provided with two valve seats 111, 111 on which two ball valves 112, 112 are provided with springs 113 therebetween.
The hydraulic path 11A is opened through the communication hole 110 between the ball valves, and the ball valve 112 on the chamber 6 side with high hydraulic pressure is pushed by the hydraulic pressure against the resilience of the spring 113. The hydraulic pressure introduced therefrom flows into the oil chamber 9C via the hydraulic pressure path 11A.

FIG. 14 also shows an oil chamber 7B formed on the back surface of the ring-shaped sealing member 7. The oil pressure guided to the oil chamber 9C is guided via a hydraulic path 11B provided in the casing cover 1A. Thus, the ring-shaped sealing material 7 is pressed against the rotor end face 3A.

In the above description, since the vertical sealing material 9 is attached to the fixed segment 4 and does not move, the horizontal sealing material 10 of the vane 5 rotates with the rotor 3.

Therefore, the ring-shaped sealing material 7 attached to the casing cover 1A receives a frictional force due to circumferential compression at a contact portion between the rotor end surface 3A and the horizontal sealing material 10, and the ring-shaped sealing material 7 is removed. This is the force to rotate.

Since the ring-shaped sealing member 7 has a circular ring shape, it is considered that the ring-shaped sealing member 7 is circumferentially moved in the accommodating groove 1C of the casing cover 1A by the frictional force.

On the other hand, since the ring-shaped sealing member 7 is also pressed against the vertical sealing member 9 of the fixed segment 4, the ring-shaped sealing member 7 is stopped by the frictional force caused by the pressing with the vertical sealing member 9. Power works.

Therefore, when the rotary vane type steering machine is operated, the ring-shaped sealing member 7 receives a complicated force of a moving force and a stopping force, and due to this force, the contact of the sealing material is caused. There is a problem that the part is unevenly worn or damaged, and the uneven wear or damage is caused by the oil chamber 6,
There is a problem that the control of the rudder becomes unstable, which is a factor of hydraulic pressure leakage between the six.

Further, there has been a problem that the worn or damaged portion is diffused over the entire circumference of the ring-shaped sealing member 7 due to the accompanying rotation. And the ring-shaped sealing material 7
13 is exposed in the oil chamber 6 as shown in FIG. 13, and may protrude into the oil chamber 6 under the influence of the above-mentioned complicated force and may be deformed. When a broken piece is generated by contact with the oil chamber, the broken piece floats and scatters in the oil chamber 6, causing a problem that the hydraulic system is clogged.

An object of the present invention is to solve the above problems and to provide a highly reliable seal system for a rotary vane type steering machine by eliminating damage to a seal portion of the rotary vane type steering machine. .

[0020]

According to the present invention, there is provided a rotary vane type steering machine, wherein a ring-shaped seal member for sealing between an inner surface of a casing end face and a rotor end face is provided. A ring-shaped substrate having a diameter smaller than the circumference of the edge of the rotor end face, wherein the ring-shaped substrate integrally has a radial projection at an outer peripheral position corresponding to the fixed segment, and seals between the fixed segment and the rotor. A vertical sealing material to be pressed against a protruding portion of the ring-shaped sealing material, and the vane base portion to a position where a horizontal sealing material for sealing between the inner surface of the casing end surface and the vane end surface contacts the outer diameter of the ring-shaped sealing material. And is extended in the radial direction of the rotor, and is pressed against the ring-shaped sealing material.

According to this configuration, the ring-shaped seal member is prevented from rotating at the radially projecting portion, and even if a force for moving the ring-shaped seal member due to contact with the lateral seal member acts, the ring-shaped seal member is housed in the housing groove at the end face of the casing. The seal member does not rotate, and the relative movement between the vertical seal member and the ring seal member is eliminated, so that the sealing property is improved.

Further, in the sealing method of the rotary vane type steering machine, the end face of the vertical sealing material for sealing between the fixed segment and the rotor is compressed on the inner face of the casing end face, and the end face angle of the vertical sealing material is caused by the compressive force. The portion is bulged toward the side surface of the ring-shaped sealing material.

According to this configuration, since the corner of the end face of the fixed segment is pressed into contact with the side surface of the ring-shaped sealing material, the gap between the vertical sealing material of the fixed segment and the ring-shaped sealing material is securely sealed.

Further, in the sealing method of the rotary vane type steering machine, the outer peripheral surface of the end portion of the horizontal sealing material which is in contact with the ring-shaped sealing material is formed to have a curved convex surface.
According to this configuration, the contact area between the ring-shaped sealing material and the horizontal sealing material is reduced, so that the frictional resistance is reduced and the abrasion damage of the ring-shaped sealing material is also reduced.

Further, in the seal system of the rotary vane type steering machine, an oil passage which is continuous in the circumferential direction is provided on a contact surface of the ring-shaped seal member with the rotor end surface.
With this configuration, the contact surface between the ring-shaped sealing member and the rotor end face is lubricated with the oil that has entered the oil passage, so that mutual rotational contact is smooth.

[0026]

Next, an embodiment of the present invention will be described. Embodiment 1 FIG. 1 is a cutaway perspective view of a main part of Embodiment 1 of the present invention, and FIG.
1 is a partial cross-sectional view taken along the line AA of FIG. 1, FIG. 3 is a partial plan view of the BB line indicating portion of FIG. 1, FIG. 4 is a partial cross-sectional view taken along the line BB of FIG.
FIG. 5 is a partial sectional view taken along line CC of FIG.

In the following, the same parts as those of the prior art are denoted by the same reference numerals, and the description thereof will be omitted. Further, the sealing structure between the casing end face and the rotor of the present invention is substantially symmetrical only in the vertical direction. Since the structure is the same, only the casing cover 1A side will be described below.

In FIG. 1, reference numeral 1A denotes a casing cover, and bolts 1D...
D is fixed. Reference numeral 2B denotes a screw hole provided in the casing 2, and hexagon socket head bolts 1D... 1D are screw-fitted.

Reference numeral 12 denotes a ring-shaped sealing material according to the present invention, which is a ring-shaped base 12A having a diameter smaller than the circumference of the edge 3B of the rotor end face 3A. As shown in FIG. 3, a radially projecting portion 12B reaching the edge 3B of the rotor end face 3A is integrally formed.

Then, as shown in an enlarged manner in FIG. 4, the end corner 9A of the vertical sealing material 9 for sealing between the fixed segment 4 and the rotor 3 has a projecting portion 12B of the ring-shaped sealing material 12.
Is pressed against the protruding end corner 12C.

In FIG. 1, reference numeral 13 denotes a horizontal sealing material according to the present invention, which seals between the inner surface of the casing cover 1A and the end face of the vane 5 similarly to the conventional horizontal sealing material 10. Numeral 13 extends in the inner diameter direction from the edge 3B of the rotor 3 to a position in contact with the outer peripheral edge 12D of the ring-shaped sealing material 12, and as shown in an enlarged view in FIG. The outer peripheral edge corner 12D of the ring-shaped sealing material 12 is pressed against the outer peripheral edge 12D.

Next, the operation of the first embodiment will be described. The space between the tip of the fixed segment 4 and the outer surface of the rotor 3 is sealed by a vertical sealing material 9, and between the ring-shaped sealing material 12 and the vertical sealing material 9, as shown in FIG. Sealing is performed by pressure contact between 12C and the end corner 9A of the vertical sealing material.

In this case, the ring-shaped sealing material 12 is shown in FIG.
As shown in FIG. 4, it is fitted into the housing groove 1C of the casing cover 1A, and is held so as not to rotate in the circumferential direction by fitting the housing groove 1C and the protruding portion 12B.

Since the casing cover 1A and the fixed segment 4 are fixed, the contact portion between the ring-shaped sealing material 12 and the vertical seal 9 is strongly pressed without relative movement, and the oil seal between the oil chambers 6, 6 is formed. Is performed reliably. Further, wear, breakage, and the like due to relative movement cannot occur.

The ring-shaped sealing material 12 and the vertical seal 9
In the pressure contact state, the ring-shaped sealing material 12 bulges in the direction of the vertical sealing material 9 or vice versa depending on the compression condition, so that any one of the contact states shown by the dotted line in FIG.

The space between the vane 5 and the inner surface of the casing 2 is sealed by a vertical seal 9B for the vane, and the casing cover 1A
The space between the inner surface and the inner surface is sealed by a horizontal seal material 13. Between the ring-shaped sealing material 12 and the horizontal sealing material 13, the horizontal sealing material 1 extended in the inner diameter direction as shown in FIGS.
3 is sealed in a state where the end corner 13A is strongly pressed against the outer peripheral corner 12D of the ring-shaped sealing material 12.

The horizontal sealing member 13 rotates together with the rotor 3 to apply a frictional force that rotates with the ring-shaped sealing member 12 with this movement. The ring-shaped sealing member 12 has a radially projecting portion 12B and a casing cover 1A. It does not rotate because it is held in the storage groove 1C.

Further, as shown in FIG. 5, the radial position where the horizontal sealing member 13 contacts the ring-shaped sealing member 12 is covered with the inner surface of the casing cover 1A at the inner diameter position from the edge 3B of the rotor 3, so Even if worn pieces due to contact are generated, it is difficult to flow out into the oil chamber 6, and obstruction such as clogging by the worn pieces is prevented.

Further, the relative peripheral speed at the time of contact is also slowed down by the reduced radius of rotation, and the degree of wear is reduced accordingly.
As described above, according to the sealing method of the rotary vane type steering device of the first embodiment, the ring-shaped sealing material 12
Is reliably prevented from rotating due to the contact of the vane 5 with the horizontal sealing material 13 and the rotor end face 3A, and uneven wear and breakage of the ring-shaped sealing material due to the conventional rotation caused by the rotation are prevented.

The case where the protrusion amount L (FIG. 3) of the projecting portion 12B of the ring-shaped sealing material 12 of the first embodiment is substantially equal to the width B of the ring-shaped sealing material 12 is shown. The same effect can be obtained even when L is set to about one half of the width B of the ring-shaped sealing material 12. Second Embodiment FIG. 6 is an enlarged sectional view of a main part of a second embodiment of the present invention, and corresponds to a sectional view taken along line BB of FIG.

In FIG. 6, the fixed segment 4 and the rotor 3
The end face 9D of the vertical seal material 9 that seals the space between the end face 9D of the vertical seal material 9A is compressed by the inner surface of the casing cover 1A. It is configured to bulge.

In order to form the bulging portion 9E, a vertical sealing material 9 longer than the fixed segment 4 is provided.
In the mounting groove 4A, and the end face 1A such as the casing cover.
To be compressed when closed.

Therefore, according to the second embodiment, the end face corner portion 9E of the vertical seal material 9 is expanded and deformed to the protruding end corner portion 12C of the ring-shaped seal material 12 to be brought into pressure contact with each other. , The pressing force between the ring-shaped sealing material 12 and the vertical sealing material 9 is increased, and the sealing is ensured. Third Embodiment FIG. 7 is an enlarged plan view of a main part of a third embodiment of the present invention, and corresponds to an enlarged plan view of a portion indicated by a C-C line in FIG.

In the figure, the outer peripheral surface 13B of the end portion of the horizontal sealing material 13 which is in contact with the outer peripheral edge 12D (see FIG. 5) of the ring-shaped sealing material 12 is formed as a curved convex surface when the rotor 3 is viewed in the axial direction.

According to the third embodiment, the horizontal sealing material 1
3 is in contact with the ring-shaped sealing material 12 at the vertex 13C of the end outer peripheral surface 13B which is a curved convex surface, so that both the contact surface and the contact pressure with the ring-shaped sealing material 12 are reduced, and
When the horizontal sealing material 13 moves and comes into contact with the ring-shaped sealing material 12, it comes into contact with the curved convex surface 13 </ b> B in a smooth state, so that the degree of wear of the ring-shaped sealing material 12 is also reduced. Fourth Embodiment FIG. 8 is an enlarged sectional view of a main part of a fourth embodiment of the present invention, and corresponds to a sectional view taken along line CC of FIG.

In the figure, an end corner 13A of a horizontal sealing material 13 which contacts an outer peripheral edge 12D of a ring-shaped sealing material 12.
Are rounded corners when viewed in the tangential direction of the rotor.

According to the fourth embodiment, the outer peripheral corner 12D of the ring-shaped sealing member 12 comes into contact with the end corner 13A of the rounded horizontal sealing member 13 so as to bite. The degree of abrasion is small because of good contact and smooth contact with the curved surface.

In the fourth embodiment, the outer peripheral surface 13B of the end portion of the horizontal seal member 13 may be formed as a curved convex surface in the axial direction of the rotor 3 as shown in FIG. Fifth Embodiment FIG. 9 is a cross-sectional view of a main part of a fifth embodiment of the present invention, which corresponds to a cross-sectional view taken along line AA of FIG. 1, and FIG.
FIG.

In FIG. 9, reference numeral 16 denotes an oil passage, and a contact surface 12E of the ring-shaped sealing member 12 with the rotor end surface 3A is
As shown in FIG. 10, they are provided continuously in the circumferential direction.
At the center of the rudder or at the left and right small steering angles, there is almost no oil pressure difference between the adjacent oil chambers 6 and 6 (see FIG. 1), and therefore the oil pressure in the oil chamber 7B is almost zero. The pressing force to the end face 3A is reduced.

Therefore, the ring-shaped sealing material 12 and the rotor 3
The oil easily penetrates into the contact surface with the oil, and the oil in the oil chamber 6 penetrates and fills the oil passage 16. In order to take a large steering angle, when the oil pressure difference between the adjacent oil chambers 6 and 6 is increased and the rotor 3 rotates greatly, high-pressure oil pressure is guided from the oil chamber 6 to the oil chamber 7B, and the rotor end face 3
A, the ring-shaped sealing material 12 is pressed,
Since oil stored in the oil passage 16 is supplied to E,
Contact surface 12E between rotor end surface 3A and ring-shaped sealing material 12
Is lubricated and friction is reduced.

Therefore, according to the sealing method of the rotary vane type steering device of the fifth embodiment, the ring-shaped sealing member 12 fixed to the casing cover 1A and the rotor end face 3
Friction with A is reduced, the generation of unreasonable stress on the ring-shaped sealing material 12 is prevented, and wear and breakage are also prevented.

The cross-sectional shape of the oil passage 16 may be, for example, a substantially semicircular shape as shown in the figure, a square shape, a triangular shape having an opening at the bottom, or the like. It can also be an article.

In each of the above embodiments, the vertical sealing material 9, the ring-shaped sealing material 12, the horizontal sealing material 13 and the like are all made of synthetic rubber or synthetic plastic having rubber-like elasticity, so that heat resistance and abrasion resistance are reduced. Excellent urethane rubber, ethylene propylene rubber, chlorosulfonated polyethylene,
Molded from butyl rubber, chloroprene rubber, acrylonitrile butadiene rubber, acrylic rubber, silicon rubber, fluorine rubber, etc. are used. Among the above, urethane rubber which can be cast and has excellent wear resistance is preferably used. . That is, according to these molding materials, a ring-shaped sealing material having a protruding portion on the outer periphery can be easily molded as long as there is a casting mold.

[0054]

As described above, according to the rotary vane type steering system sealing method of the present invention, the ring-shaped sealing member for sealing between the inner surface of the casing cover and the rotor end surface is fixed to the casing cover. Since it does not rotate with the horizontal seal of the vane and the rotor, the seal between the vertical seal of the fixed segment and the vertical seal of the fixed segment is assured, and unreasonable external force is not applied to the ring-shaped sealing material from the vertical seal, causing uneven wear and damage Can be prevented.

Further, since the contact portion of the vane with the horizontal seal is located inside the rotor end face, the ring-shaped sealing material is protruded and deformed into the oil chamber, and the protruding portion of the rotor or the fixed segment is caused. Therefore, even if damage occurs, it is difficult to diffuse into the oil chamber, and the relative peripheral speed is lower than that of the outer periphery of the rotor, so that the frictional force is reduced accordingly.

Further, by making the contact surface of the horizontal seal of the vane with the ring-shaped sealing material a convex surface, the frictional resistance applied to the ring-shaped sealing material can be reduced, and wear and breakage of the ring-shaped sealing material due to friction can be reduced. Can be prevented.

Further, by providing an oil passage on the rotor contact surface of the ring-shaped sealing material, the friction between the fixed ring-shaped sealing material and the rotor end face is reduced, so that stress is forcibly generated in the ring-shaped sealing material. Instead, it has various effects such as a reduction in wear of the contact surface.

[Brief description of the drawings]

FIG. 1 is a cutaway perspective view of a main part of a rotary vane type steering device according to an embodiment of the present invention.

FIG. 2 is an enlarged sectional view of a main part taken along line AA of FIG.

FIG. 3 is an enlarged plan view of a portion indicated by a line BB in FIG. 1;

FIG. 4 is an enlarged sectional view of a main part taken along line BB of FIG. 1;

FIG. 5 is an enlarged sectional view of a main part taken along line CC of FIG. 1;

FIG. 6 is BB in FIG. 1 of Embodiment 2 of the present invention;
It is a principal part expanded sectional view corresponding to a line sectional view.

FIG. 7 is a sectional view taken along line BB in FIG. 1 of Embodiment 3 of the present invention;
FIG. 4 is an enlarged plan view corresponding to a portion indicated by a line.

FIG. 8 is a sectional view taken on line CC in FIG. 1 of Embodiment 4 of the present invention;
It is a principal part expanded sectional view corresponding to the part shown by the line.

FIG. 9 is a sectional view taken along line AA in FIG. 1 of Embodiment 5 of the present invention;
It is a principal part expanded sectional view corresponding to the part shown by the line.

FIG. 10 is a bottom view of a ring-shaped sealing material according to a fifth embodiment of the present invention.

FIG. 11 is a plan view showing the internal structure of a conventional rotary vane type steering gear.

FIG. 12 is a sectional view taken along line DD in FIG. 11;

FIG. 13 is a partially enlarged sectional view taken along line EE of FIG. 11;

FIG. 14 is a partially enlarged view of a portion F in FIG. 12;

15 is a partially enlarged view of a portion G in FIG.

[Explanation of symbols]

 Reference Signs List 1A Casing cover 1B Casing bottom surface 1C Storage groove 2 Cylindrical casing 3 Cylindrical rotor 3A Rotor end face 3B Edge of rotor end face 4 Fixed segment 5 Vane 6 Oil chamber 6A Oil port 7B Oil chamber 9 Vertical seal material for fixed segment 9A Vertical End corner of sealing material 9B Vertical seal for vane 9C Oil chamber 12 Ring-shaped sealing material 12A Ring-shaped base 12B Radially projecting portion 12C Projecting end corner 13 13 Horizontal sealing material 13A of the present invention 13A Corner of horizontal sealing material

[Procedure amendment]

[Submission date] March 18, 1998

[Procedure amendment 1]

[Document name to be amended] Drawing

[Correction target item name] Fig. 8

[Correction method] Change

[Correction contents]

FIG. 8

 ────────────────────────────────────────────────── ─── Continued on the front page (72) Inventor Takashi Morimoto 1-1-15 Shigino Nishi, Joto-ku, Osaka-shi, Osaka Park Sawaka Japan Hamworth Co., Ltd. In-house

Claims (4)

[Claims] A plurality of cylindrical rotors are coaxially supported in a cylindrical casing whose both end surfaces are sealed, and a space between the inner surface of the casing and the outer surface of the rotor projects from the inner surface of the casing and comes into contact with the outer surface of the rotor. A plurality of oil chambers are formed in the circumferential direction by a fixed segment and a plurality of vanes projecting from the outer surface of the rotor and coming into contact with the inner surface of the casing to form a plurality of oil chambers. In the rotary vane type steering machine, the ring-shaped sealing material for sealing between the inner surface of the casing end face and the rotor end face is a ring-shaped base having a diameter smaller than a circumference of an edge of the rotor end face. , A shape integrally having a radial projection at an outer peripheral position corresponding to the fixed segment, A vertical sealing material that seals the space between the casing and the ring-shaped sealing material, and a horizontal sealing material that seals between the inner surface of the casing end face and the vane end face contacts the outer diameter of the ring-shaped sealing material. A rotary vane type steering machine sealing system extended from the vane base to the inner diameter direction of the rotor and pressed against the ring-shaped sealing material. 2. An end face of a vertical sealing material for sealing between a fixed segment and a rotor is compressed on an inner face of an end face of a casing, and a corner of an end face of the vertical sealing material bulges toward a side face of the ring-shaped sealing material due to the compressive force. The seal system for a rotary vane type steering machine according to claim 1, wherein the seal system is used. 3. The sealing method for a rotary vane type steering machine according to claim 1, wherein an outer peripheral surface of an end portion of the horizontal sealing material in contact with the ring-shaped sealing material has a curved convex surface. 4. A seal system for a rotary vane type steering machine according to claim 1, wherein an oil passage continuous in the circumferential direction is provided on a contact surface of the ring-shaped seal member with the rotor end surface.