JPH0932932A - Edge type rotary shaft seal device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To reduce the abrasion of a slide material and improve durability by lessening a sliding part at high speed rotation. SOLUTION: This seal device has a mating ring 4 mounted on a rotary shaft 2, with thick and thin parts 4b and 4c alternately formed continuously in a peripheral direction and one side formed as a smooth seal surface 4d, and a seal ring 8 fitted to a housing 5, with the edge pressed to the seal surface 4d of the mating ring 4 in such a state as pushed with an energizing member 6.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an end face type rotary shaft seal device, and more particularly to an end face type rotary shaft seal device for sealing between both ends of a shaft rotating at high speed.

[0002]

2. Description of the Related Art Generally, an end face type rotary shaft sealing device 31 for sealing between both ends of a shaft which rotates at a high speed is constructed as shown in FIG.

A sleeve 33 is provided on the outside of the rotary shaft 32.
The mating ring 34 is integrally fixed via
It rotates integrally with the rotary shaft 32.

A fixed portion X is provided with a predetermined distance from the rotary shaft 32.
A bellows 36 that surrounds the outside of the rotary shaft 32, and a bellows 36 that is fixed to the housing 35 that is fixed to the
A seal ring 38 that surrounds the outside of the rotary shaft 32 is provided via a fixed ring 37 attached to the end of the rotary shaft 32.

A protruding portion 38a is provided on a side surface of the seal ring 38 opposite to the fixed ring 37. The protruding portion 38a is a side surface of the mating ring 34.
d.

The end face type rotary shaft sealing device 31 as described above
In this case, it is used as a shaft seal for the rotating shaft of rotating equipment, and the most typical equipment used is an aircraft jet engine. A jet engine compresses air and sends it to a combustion chamber where it is mixed with fuel for combustion, and the turbine rotated by the combustion gas is held by bearings, and lubricating oil is supplied to these bearings.

On the other hand, inside the engine, there is air compressed by the compressor and burned gas, and these also invade the bearing portion due to pressure, so it is necessary to separate the lubricating atmosphere of the bearing from the invading gas. An end face type rotary shaft sealing device 31 is used as this partition. in this case,
Since the pressure of the invading gas is higher than that of the lubricated bearing portion, it becomes a gas seal.

Therefore, in FIG. 11, the P1 side is the gas chamber of the high pressure gas atmosphere, and the P2 side is the bearing chamber of the low pressure lubricating atmosphere, and the sealing surface 3 of the mating ring 34 is used.
4d and the end surface of the protruding portion 38a of the seal ring 38 rotationally slide, and dynamic sealing is performed at this portion.

The pressure on the gas chamber P1 side is combined with the spring load of the bellows 36 and applied to the seal sliding surface, and the seal sliding surface generates heat by sliding. This heat generation amount increases as the rotation of the shaft increases. In order to prevent the heat of the sliding portion from causing the material of the sliding portions of the seal ring 38 and the mating ring 34 to exceed the thermal limit and to not rapidly wear, an oil is added to remove the heat generated in the sliding portion. The jet 39 is effective.

That is, an oil jet 39 having a low temperature is jetted to the mating ring 34 to cool it, whereby a large amount of gas on the high pressure side leaks into the bearing chamber without sudden abrasion of the material of the sliding portion. Works like no.

In recent years, the engine speed has been increased (higher speed), and this speed increase has exceeded the performance limit of the conventional end face type rotary shaft seal device. When the conventional end face type rotary shaft seal device is used for such an engine, the following problems occur and it cannot be practically used.

Rotating shaft 32 of end face type rotating shaft sealing device 31
The sliding parts of and generate heat by sliding. Since this heat generation amount increases as the number of rotations increases, a material with a high thermal limit is used as the material, or the pressure balance between the sliding diameter of the seal ring and the effective diameter of the bellows on which the differential pressure acts. Is taken to reduce the load.

However, as the engine speed increases, the sliding speed increases, and at the same time the seal pressure rises, the load on the rotary sliding part exceeds the limit of the sliding material, and the wear and the life end in a short time. .

Further, even if the mating ring 34 is cooled by the oil jet 39 having a low temperature in order to remove the heat generated in the sliding portion, there is a limit to the efficient cooling due to the indirect cooling. The usage environment, that is, high speed and high pressure, exceeds the applicable limit.

An object of the present invention is to reduce the amount of heat generated by sliding by reducing the size of the rotary sliding portion that seals when the engine speed increases, so that the thermal limit of the sliding material is not exceeded. An object of the present invention is to provide an end face type rotary shaft seal device capable of improving durability. Another object of the present invention is to reduce the sliding heat generation of the sliding portion and reduce the influence of the sliding heat generation due to the cooling action of the oil jet on the mating ring.
An object of the present invention is to provide an end face type rotary shaft sealing device that can be applied with a wide range while improving durability.

[0016]

In order to achieve the above-mentioned object, the present invention provides a housing provided in a fixed portion,
The housing includes a mating ring that is provided on a rotary shaft and that rotates integrally, and a seal ring and a biasing member that biases the seal ring are provided in the housing, and the seal ring is a bellows. In an end face type rotary shaft seal device which is pressed against the end face of the seal ring to seal the mating ring, the thick part and the thin part are alternately continuous in the circumferential direction, and the end face is in contact with the seal ring. The end face type rotary shaft sealing device is characterized by being formed into a smooth surface.

Further, according to the present invention, there is provided a housing provided on the fixed portion and a mating ring provided on the rotary shaft and rotating integrally with the housing. The seal ring and the seal ring are biased to the housing. And a biasing member for
In an end face type rotary shaft seal device in which the seal ring is pressed against the end face of the mating ring by a bellows to seal the mating ring, the thick part and the thin part are alternately continuous in the circumferential direction. In addition, the end face contacting with the seal ring is formed into a smooth surface, and the oil jet is jetted to the mating ring.

A means in which the thick portion and the thin portion of the mating ring are gently changed is adopted, or a plurality of mating rings are provided outwardly in the circumferential direction with a predetermined interval. By providing the holes of the above in a state of being opened on the outer peripheral surface, a thick portion is formed between the holes, and a thin portion is formed on the side of each hole so that an oil jet can be injected into each hole. In addition, a means was adopted in which the direction of the thick portion and the thin portion was in the range of 0 ° to ± 90 ° with respect to the radial direction.

[0019]

According to the present invention, the above means are adopted.
When the rotary shaft starts to rotate, the mating ring also starts to rotate integrally and starts sliding with respect to the seal ring.
Since the mating ring has thick and thin portions that are alternately formed continuously, it deforms due to sliding heat generated during rotation, and only the thick portion contacts the seal ring and corresponds to the thin portion. And a wedge-shaped gap is formed between the two parts, or only a thin part contacts the seal ring and a wedge-shaped gap is formed between the thin part and a part corresponding to the thick part. This becomes more remarkable as the rotation axis becomes faster. Therefore, when the rotating shaft rotates at high speed, the sliding part, which is the seal part, becomes smaller, so the amount of heat generated by sliding decreases and the thermal limit of the sliding material is not exceeded. Become.

Further, when the rotating shaft rotates at a high speed, the sliding portion becomes smaller, so that the amount of heat generated by sliding decreases and the thermal limit of the sliding material is not exceeded. In addition to the small amount of dynamic heat generation, the cooling effect of the oil jet on the mating ring reduces the effect of sliding heat generation, which improves durability and
The application range can be widened.

Further, a wedge-shaped gap is formed by changing the thick portion and the thin portion of the mating ring into a gentle mountain shape, or holes are provided at predetermined intervals in the circumferential direction. By forming a thick portion between the holes and a thin portion at the outer peripheral portion forming each hole, it is possible to inject an oil jet into the inside of the hole. If the direction of the thick portion and the thin portion is in the range of 0 ° to ± 90 ° with respect to the radial direction of the rotating shaft, a gap can be generated and sliding heat generation can be reduced.

[0022]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of the present invention shown in the drawings will be described below. FIG. 1 shows a schematic sectional view of an end face type rotary shaft seal device 1 according to the present invention. A mating ring 4 is integrally fixed to the rotary shaft 2 via a sleeve 3 on the outer side thereof.

A bellows 6 surrounding the outside of the rotary shaft 2 is attached to a housing 5 fixed to the fixed portion X with a predetermined distance from the rotary shaft 2, and attached to the end portion of the bellows 6. A seal ring 8 that surrounds the outside of the rotary shaft 2 is provided via a fixed ring 7 that is located.

A projecting portion 8a is formed on a side surface of the seal ring 8 opposite to the fixed ring 7, and an end surface of the projecting portion 8a is a sealing surface 4d which is an end surface of the mating ring 4.
Is in contact with

The P1 side is a gas chamber in a high pressure gas atmosphere, and the P2 side is a bearing chamber in a low pressure lubricating atmosphere.
As shown in FIG. 5, the sealing surface 4d, which is the end surface of the mating ring 4, and the end surface of the protruding portion 8a, which is the end surface of the seal ring 8, rotate and slide, and dynamic sealing is performed between them.

Further, the mating ring 4 is shown in FIG.
As shown in FIG. 3, the base 4a is attached to the rotary shaft 2 and has a constant thickness, and a thick portion 4b and a thin portion 4c are provided continuously on the outer peripheral side alternately in the circumferential direction. Has been done. The thick portion 4b and the thin portion 4c are smooth on their seal ring 8 sides and are formed on the sealing surface 4d.

2 is a schematic perspective view of the mating ring 4, and FIG. 3 is a view taken in the direction of arrow D in FIG. 4 and 5 are sectional views taken along the line CC of FIG. The number of the thick portions 4b and the thin portions 4c can be set arbitrarily, the thickness is also arbitrary, and further, the width in the circumferential direction and the length in the axial direction can be set arbitrarily. .

The end face type rotary shaft seal device 1 as described above is used as a shaft seal for the rotary shaft 2 of a rotary machine. Then, as the rotary shaft 2 rotates, the sleeve 3 and the mating ring 4 integrally fixed to the rotary shaft 2 by the sleeve 3 also rotate.

The sealing surface 4d, which is the end surface of the mating ring 4, is in sliding contact with the end surface of the protruding portion 8a of the seal ring 8 which is biased and pressed by the bellows 6, and the sliding contact results in the sealing. It is designed to be effective. That is, the differential pressure that acts acts on the seal surface 4d of the mating ring 4 and the protruding portion 8a of the seal ring 8.
Sealed between the end face of In addition, P1 is a high pressure side such as a gas chamber, and P2 is a low pressure side such as a bearing chamber.

In the conventional end face type rotary shaft seal device 31, since the mating ring 34 has a uniform thickness, the sliding speed increases due to the increase in the rotation speed, and the pressing load against the seal sliding portion due to the increase in the seal pressure. The amount of heat generated by sliding increases in the sliding portion, which is the sealing surface, and the temperatures of the seal ring 8 and the mating ring 4, which are sliding materials, rise.

The temperature rise due to sliding heat generation of this seal causes thermal deterioration of the sliding material, leading to early wear of the sliding portion and deterioration of the roughness and sliding surface accuracy of the sliding portion necessary as a seal. The life of the seal is significantly reduced.

However, in the case of the present invention, since the mating ring 4 is composed of the thick portion 4b and the thin portion 4c, when the temperature rises due to the sliding heat generation, as shown in FIG. Transform as shown.

The thin portion 4 of the mating ring 4
When c is displaced as shown in FIG. 4, a wedge-shaped gap A is formed between the seal surface 4d of the mating ring 4 and the end surface of the protruding portion 8a of the seal ring 8.

The gap A gradually increases toward the rear in the rotation direction of the mating ring 4, and the first half portion A1 increases.
And the latter half A2 which becomes smaller in sequence. Then, a dynamic pressure effect as shown in FIG. 4 is generated in the latter half portion A2, and the sliding load of the seal ring 8 is reduced by this dynamic pressure effect, so that it is possible to prevent the thermal limit of the material from being exceeded, Wear can be prevented.

The first half A1 of the gap A is the second half A
Although a dynamic pressure in the opposite direction of 2 is generated, the theoretical maximum pressure is a vacuum (actually, it is a much smaller dynamic pressure), and since it does not exceed this, the latter half part A
The dynamic pressure of 2 will be obtained in the overcoming condition.

The thin portion 4c of the mating ring 4
The mating ring 4 when it is displaced as shown in FIG.
A wedge-shaped gap A is formed between the sealing surface 4d and the end surface of the protruding portion 8a of the seal ring 8.

The clearance A is gradually increased toward the rear in the rotation direction of the mating ring 4, and the first half A1 is gradually increased.
And the latter half A2 which becomes smaller in sequence. Then, a dynamic pressure effect as shown in FIG. 5 is generated in the latter half portion A2, and the sliding load of the seal ring 8 is reduced by this dynamic pressure effect, so that it is possible to prevent the thermal limit of the material from being exceeded, and to rapidly Wear can be prevented.

The first half A1 of the gap A is the second half A
Although a dynamic pressure in the opposite direction of 2 is generated, the theoretical maximum pressure is a vacuum (actually, it is a much smaller dynamic pressure), and since it does not exceed this, the latter half part A
The dynamic pressure of 2 will be obtained in the overcoming condition.

That is, in the high-speed high-load seal, the thin portion 4c of the mating ring 4 is deformed by sliding heat generation as shown in FIG. Then, the pressing load between the sealing surface 4d of the mating ring 4 and the end surface of the protruding portion 8a of the sealing ring 8 is reduced. As a result, the sealing surface 4d of the mating ring 4 can be brought into a thermal non-uniform temperature state, and a wedge-shaped gap A is generated by thermal deformation, and a dynamic pressure effect is generated by this gap A, and the seal This is to reduce the load.

In the above case, by cooling with the oil jet 9, the temperature rise of the sliding surface can be suppressed and effective heat removal can be performed. Due to the cooling effect of this oil jet 9, a temperature non-uniform state can be intentionally created, and the seal surface can be further thermally deformed.

This is because the mating ring 4 has a thick portion 4
By forming b and the thin portion 4c, the thin portion 4c is contracted more than the thick portion 4b by cooling with good heat transfer, and the gap A is maintained in a wedge shape.

As described above, the dynamic pressure action obtained from the wedge-shaped gap A obtained by the deformation of the mating ring 4 with temperature suppresses the increase of the sliding load between the mating ring 4 and the seal ring 6, The range of application can be greatly expanded.

Further, the thick portion 4 of the mating ring 4
By changing the size of b or the thin portion 4c, or changing the number, it is possible to adjust the dynamic pressure most suitable for the application condition of the seal.

FIG. 6 shows a schematic sectional view of another embodiment of the end face type rotary shaft seal device 1 according to the present invention. As with the above embodiment, the rotary shaft 2 has a sleeve 3 on its outer side.
The mating ring 4 is integrally fixed via.

The housing 5 has a base portion 5a fixed to the fixed portion X and a tubular portion 5b surrounding the rotary shaft 2, and the base portion 5a has a shaft 10 extending parallel to the rotary shaft 2. The fixing ring 7 is provided and has a distal end portion of the shaft 10 having a tubular portion 7b surrounding the tubular portion 5b of the housing 5.
A spring 11 that penetrates the base portion 7a of the housing 5 and that acts to separate the base portion 5a of the housing 5 from the base portion 7a of the fixing ring 7 is provided on the outside.

Reference numeral 12 is a pin for preventing the fixed ring 7 from coming off, and 13 is a ring for sealing between the tubular portion 5b of the housing 5 and the tubular portion 7b of the fixed ring 7 in this embodiment. Uses two seals 13.

The fixed ring 7 is provided with a seal ring 8 surrounding the outside of the rotary shaft 2. A protruding portion 8a is formed on the side surface of the seal ring 8 on the mating ring 4 side, and the end surface of the protruding portion 8a abuts on the seal surface 4d which is the end surface of the mating ring 4. It depends on the urging force of the spring 11, which is a member.

The P1 side is a gas chamber in a high pressure gas atmosphere, and the P2 side is a bearing chamber in a low pressure lubricating atmosphere.
As shown in FIG. 5, the sealing surface 4d, which is the end surface of the mating ring 4, and the end surface of the protruding portion 8a, which is the end surface of the seal ring 8, rotate and slide, and dynamic sealing is performed between them.

Further, the mating ring 4 is shown in FIG.
It is similar to that shown in FIG. 3 and is formed of a base portion 4a having a constant thickness, and a thick portion 4b and a thin portion 4c which are continuously provided alternately on the outer peripheral side in the circumferential direction. The thick portion 4b and the thin portion 4c are smooth on their seal ring 8 sides and are formed on the sealing surface 4d.

2 is a schematic perspective view of the mating ring 4, and FIG. 3 is a view taken in the direction of arrow F in FIG. 4 and 5 are sectional views taken along the line EE of FIG. The number of the thick portions 4b and the thin portions 4c can be set arbitrarily, the thickness is also arbitrary, and further, the width in the circumferential direction and the length in the axial direction can be set arbitrarily. This is the same as the above embodiment.

The end face type rotary shaft seal device 1 as described above is used as a shaft seal for the rotary shaft 2 of a rotary machine. Then, as the rotary shaft 2 rotates, the sleeve 3 and the mating ring 4 integrally fixed to the rotary shaft 2 by the sleeve 3 also rotate.

The sealing surface 4d, which is the end surface of the mating ring 4, is in sliding contact with the end surface of the projecting portion 8a of the seal ring 8, and this sliding contact exerts a sealing effect. That is, the acting differential pressure is sealed between the sealing surface 4d of the mating ring 4 and the end surface of the protruding portion 8a of the sealing ring 8. In addition, P1 is a high pressure side such as a gas chamber, and P2 is a low pressure side such as a bearing chamber.

The rotation of the seal ring 8 with the mating ring 4 during operation is prevented by the shaft 10 blocking the rotation of the fixed ring 7 with respect to the housing 5. In addition, the sealing surface 4d of the mating ring 4
The pressing force of the protruding portion 8a of the seal ring 8 against the spring 1
It can be arbitrarily set by 1.

When sliding heat is generated during operation, the mating ring 4 is deformed as shown in FIG. 4 or 5 to form a wedge-shaped gap A as shown in FIG. It can be prevented from being abruptly worn. Further, by using the oil jet 9, the seal surface can be further thermally deformed, the gap A can be maintained in a wedge shape, an increase in sliding load can be suppressed, and the range of application can be greatly expanded.

FIG. 7 shows another example of the mating ring 4, in which the thick portion 4b and the thin portion 4c are formed in a saw shape. Even with this structure, the thin portion 4c is rotated.
Is deformed to form a gap, and the load on the seal can be reduced.

FIGS. 8 and 9 show still another example of the mating ring 4, in which holes 4e are provided in the circumferential direction, and a thick portion 4b is formed between the adjacent holes 4e and a hole 4e is formed. Each of the thin portions 4c is formed, and a protrusion 4f is formed on the base 4a opposite to the seal ring 8.
The hole 4e is opened in the base portion 4a on the inner diameter side of f.

When the mating ring 4 is formed as described above, the thin portion 4c formed between the hole 4e and the seal surface 4d due to the oil jet 9 flowing in the hole 4e is the adjacent hole 4e. The heat generated in the sealing surface 4d can be removed more efficiently than in the thick portion 4b formed between them, and as a result, the wedge-shaped gap A is formed by deformation.
Therefore, the range of application can be greatly expanded.

As the shape of the mating ring 4 which obtains the dynamic pressure effect as described above, the thick portion 4b and the thin portion 4c of FIGS. 3 and 7, and the hole 4e through which the cooling fluid which is the oil jet of FIG. 8 passes. Thick part 4b formed by
When the thin portion 4c is in a range of a predetermined angle θ from the state in which the thin portion 4c is along the radial direction, the dynamic pressure effectively acts.

That is, as shown in FIG. 10, even if the radial direction is set to 0 ° and the thick portion 4b and the thin portion 4c are formed by forming an angle θ within a range of ± 90 ° from this, the wedge-shaped gap is effective. Can be formed. Furthermore, the thick portion 4
The b and the thin portion 4c are not limited to the illustrated shapes, and various shapes can be adopted. The point is that the mating ring 4 is provided with the thick portion 4b and the thin portion 4c, and It suffices to generate a dynamic pressure during pressing to reduce sliding heat generation.

Although the bellows 6 and the spring 11 are used as the means for pressing the seal ring 8 against the mating ring 4 in each of the above-mentioned embodiments, the present invention is not limited to this, and various biasing means may be used. Can be used.

[0061]

In the end face type rotary shaft seal device according to the present invention, the circumferential predetermined portion of the mating ring is separated from the end face of the seal ring by the centrifugal force generated by the rotation or the portion thereof. Since only the abutting parts contact with each other, the sliding portion is reduced and the amount of heat generated is reduced. This makes it possible to prevent the thermal limit of the material from being exceeded, prevent wear, and enhance durability.

Further, in addition to reducing the amount of sliding heat generated due to the reduction of sliding parts caused by rotation, the effect of sliding heat generation is achieved by injecting an oil jet toward the inner diameter side of the mating ring for cooling. Even less,
This has the effects of improving durability and widening the range of application.

Further, by changing gently between the thick part and the thin part of the mating ring, the wedge-shaped gap can be increased as compared with the case where the gap does not change smoothly, and the optimum dynamic pressure can be obtained. Can be set to effect. By providing a hole inside the mating ring, it is possible to inject an oil jet into the hole to improve cooling efficiency. If the direction of the thick portion and the thin portion is in the range of 0 ° to ± 90 ° with respect to the axial direction of the rotating shaft, centrifugal force acts on the thick portion when the mating ring is rotated by the rotation of the rotating shaft. As a result, the thick portion can bulge outward, and a dynamic pressure effect can be obtained.

Further, since the above effect can be exhibited only by changing the mating ring, it is possible to install the conventional sealing device only by changing the mating ring. It has the effect of being able to.

[Brief description of drawings]

FIG. 1 is a schematic cross-sectional view showing an entire end face type rotary shaft sealing device of the present invention.

FIG. 2 is a schematic perspective view of a mating ring.

3 is a view taken in the direction of arrow D in FIG. 1 and a view taken in the direction of arrow F in FIG.

FIG. 4 is a schematic view showing a state in which a mating ring is deformed in one direction due to sliding heat generation.

FIG. 5 is a schematic view showing a state in which the mating ring is deformed in another direction due to sliding heat generation.

FIG. 6 is a schematic sectional view showing the whole of another embodiment of the end face type rotary shaft seal device of the present invention.

FIG. 7 is a schematic view showing another example of a mating ring.

FIG. 8 is a schematic view showing still another example of a mating ring.

9 is a cross-sectional view showing a state in which the one shown in FIG. 8 is attached to a rotary shaft.

FIG. 10 is a schematic view showing a state where a boundary between a thick portion and a thin portion of the mating ring is inclined with respect to the radial direction.

FIG. 11 is a schematic view showing an entire conventional end face type rotary shaft sealing device.

[Explanation of symbols]

 1, 31 ... end face type rotary shaft seal device 2, 32 ... rotary shaft 3, 33 ... sleeve 4, 34 ... mating ring 4a, 5a, 7a ... base 4b ... thick part 4c ... thin Part 4d, 34d ... Sealing surface 4e ... Hole 4f ... Projection part 5, 35 ... Housing 5b, 7b ... Cylindrical part 6, 36 ... Bellows 7, 37 ... Fixing ring 8, 38 ... Seal Ring 8a, 38a ...... Projection 9,39 ...... Oil jet 10 ...... Shaft 11 ...... Spring 12 ...... Pin 13 ...... Seal X ...... Fixed part A ...... Wedge-shaped gap A1 ...... First half of gap A2 …… The latter half of the gap P1 …… Gas chamber P2 …… Bearing chamber

Claims (7)

[Claims] 1. A housing (5) provided on a fixed portion (X), and a mating ring (4) provided on a rotating shaft (2) and integrally rotating, wherein the housing (5) is provided. , A seal ring (8) and an urging member (6, 11) for urging the seal ring (8), and the seal ring (8) is urged by the urging member (6, 11). In the end face type rotary shaft sealing device which is pressed against the end face of (4) to seal, the mating ring (4) is provided with a thick portion (4b) and a thin portion (4c) alternately in the circumferential direction. And an end face (4d) that is in contact with the seal ring (8) is formed into a smooth surface. 2. A housing (5) provided on a fixed part (X), and a mating ring (4) provided on a rotating shaft (2) and integrally rotating, wherein the housing (5) is provided. , A seal ring (8) and an urging member (6, 11) for urging the seal ring (8), and the seal ring (8) is urged by the urging member (6, 11). In the end face type rotary shaft sealing device which is pressed against the end face of (4) to seal, the mating ring (4) is provided with a thick portion (4b) and a thin portion (4c) alternately in the circumferential direction. And the end face (4d) that abuts the seal ring (8) is formed into a smooth surface, and an oil jet (9) is jetted to the mating ring (4). End face type rotary shaft seal device . 3. The end surface type rotary shaft seal device according to claim 1, wherein the urging member is formed of a bellows (6). 4. The end face type rotary shaft seal device according to claim 1, wherein the biasing member is formed of a spring (11). 5. The end face type rotary shaft seal device according to claim 1, wherein the portion between the thick portion (4b) and the thin portion (4c) of the mating ring (4) changes gently. 6. The mating ring (4) has a plurality of holes (4) facing outward in the circumferential direction and spaced at predetermined intervals.
e) is provided on the outer peripheral surface so that each hole (4e)
A thick portion (4b) is formed between them and a thin portion (4c) is formed at the side of each hole (4e), and an oil jet (9) can be injected into each hole (4e). Item 1. An end face type rotary shaft sealing device according to items 1 and 2. 7. The end face type rotary shaft according to claim 1, wherein the direction of the thick portion (4b) and the thin portion (4c) is in the range of 0 ° to ± 90 ° with respect to the radial direction. Sealing device.