JPH0914455A - Rotary shaft sealing device - Google Patents

Abstract

PURPOSE: To reduce abrasion of a sliding material so as to improve durability by reducing the area of a part which is slid at the time of high speed rotation. CONSTITUTION: In a rotary shaft sealing device 1 arranged on a housing 5 and having a seal ring kit 9 which consists of a seal ring 6, a cover ring 7, an extension spring 8, a key, and the like, and a seal runner 4 installed on a rotary shaft 2 and which is brought in sliding-contact with the seal ring 6 on an outer peripheral surface, the seal runner 4 is formed in such a way that a wall thickness part and a wall thin part are continued to alternately.

Description

Detailed Description of the Invention

[0001]

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

[0002]

2. Description of the Related Art Generally, a rotary shaft sealing device 31 for sealing between both ends of a shaft which rotates at a high speed.
In this case, it is configured as shown in FIG.

A sleeve 33 is provided on the outside of the rotary shaft 32.
The seal runner 34 is integrally fixed via the shaft and rotates integrally with the rotary shaft 32.

A fixed portion X is provided with a predetermined distance from the rotary shaft 32.
The seal runner 3 is attached to the housing 35 fixed to the
4, a seal ring 36 that surrounds the outside of the seal ring 4, a cover ring 37 that surrounds the outside of the seal ring 36, an annular extension spring 38 that biases the cover ring 37 inward, and a seal ring 36. A seal ring kit 39 including a key (not shown) for fixing between the cover ring 37 and the cover ring 37 is provided. The key of the seal ring kit 39 is fixed to the housing 35 by a rotation lock pin (not shown).

The seal ring 36 is a ring divided into two or more parts in the circumferential direction, and is held in contact with the outer peripheral surface of the seal runner 34 attached to the rotary shaft 32 with the same curvature. The cover ring 37 is a ring divided into two or more parts in the circumferential direction, and is held in contact with the outer peripheral surface of the seal ring 36 with the same curvature. Seal ring 36
A plurality of grooves 36a extending in the axial direction are provided on the inner peripheral surface of the housing 35, leaving a part on the side in contact with the housing 35, and a circumferential groove 36b communicating the grooves 36a on the housing 35 side (FIG. 10). reference). Similarly, a groove 36c is also provided on the housing side surface of the seal ring 36.

The split portion of the seal ring 36 has a step split structure to eliminate a gap in the axial direction. That is, when the seal ring 36 is set on the outer peripheral portion of the seal runner 34, the gap a widens in the circumferential direction in the divided portion (see FIG. 10). Note that, in FIG. 10, the gap a is shown to be larger than in the state in which it is set on the outer peripheral portion of the seal runner 34.

A cover ring 37 is located on the outer periphery of the seal ring 36 and covers the divided portion of the seal ring 36 in a state in which the phase of the divided portion is circumferentially shifted so as to close the gap a.

Seal ring 36 and cover ring 37
With the structure divided in the circumferential direction, it is possible to follow the dimension with respect to the shaft, and further to follow sliding displacement and wear. Then, it is possible to always slide on the shaft or follow the seal through a minute fluid film. The follow-up amount due to wear (wear allowance) depends on the gap a of the divided portion.

The compression spring 40 axially presses the seal ring kit 39 through the plate 41, presses the end surface of the seal ring 36 against the housing 35, and applies a necessary seal load in the initial stage.

The extension spring 38 presses the seal ring 36, the cover ring 37, and the key in the radial direction and mounts them on the rotary shaft 32. In this state, the seal load required at the initial stage is applied to the sliding portion. .

Reference numeral 43 is a spring retainer for holding the compression spring 40, and 42 is a snap ring for holding the spring retainer 43 in the housing 35.

In the rotary shaft seal device 31 as described above, it is used as a shaft seal of the rotary shaft of a rotary machine, and the most typical machine 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, there is air compressed by the compressor and burned gas inside the engine, 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. The 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, a gas seal is formed.

Therefore, in FIG. 9, the P2 side serves as a bearing chamber, and the bearing is lubricated by the oil jet 44, which is a lubrication system in which oil is injected from a nozzle. In the engine, the pressure in the gas chamber P1 rises in proportion to the rotation, and the temperature rises. The inner surface of the seal ring 36 and the outer surface of the seal runner 34 slide while sealing therebetween. Heat is generated due to sliding, and the amount of heat generated increases as the number of rotations increases. An oil jet 44 having a low temperature is jetted inside the seal runner 34 to cool it so that the material of the sliding portion between the seal ring 36 and the seal runner 34 does not exceed the thermal limit and wear does not rapidly progress.

Thus, the material of the sliding portion is not abruptly worn, and the gas on the high pressure side is prevented from leaking into the bearing chamber in a large amount. The acting differential pressure is sealed by the seal dams 45 and 46 of the seal ring 36. The seal dam 45 is for sealing with the seal runner 34, and the seal dam 46 is for sealing with the housing 35.

The seal dams 45, 46 of the seal ring 36
In order to reduce the fluid force due to the differential pressure, the groove 36a, 36b, 36c for pressure balance is formed as described above, so that the structure has a very small width. When the differential pressure is small, the pressure balancing grooves 36a, 36b, 36c provided on the inner peripheral surface or the end surface of the seal ring are not necessary, and the seal ring 36 is formed on a flat inner peripheral surface without grooves. The contact surface of the seal ring 36 with the housing 35 is the rotation shaft 3
It slides while relatively sliding with respect to the radial displacement generated following the rotational shake of 2. The oil jet 44 cools the inner diameter side of the seal runner 34 and then is discharged by centrifugal force.

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

The sliding portion of the rotary shaft sealing device 31 with the rotary shaft 32 generates heat by sliding. Since this heat generation amount increases with an increase in the number of rotations, a material having a high thermal limit is used as the material, or as described above, the seal ring 36 is provided with the pressure balancing grooves 36a, 36b, 36c. To reduce the load. However, as the engine speed increases, the sliding speed increases, and at the same time, the seal pressure increases, and the load on the rotary sliding portion exceeds the limit of the sliding material, causing wear in a short time and reaching the end of its life. Further, even in the structure in which the oil jet having a low temperature is used to cool the inner diameter side of the seal runner in order to remove the heat generated in the sliding portion, there is a limit to cooling, and the usage environment 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 so that the thermal limit of the sliding material is not exceeded when the engine runs at high speed.
Accordingly, it is an object of the present invention to provide a rotary shaft seal device capable of improving durability. Another object of the present invention is that the sliding heat generation amount of the sliding portion is small and the influence of the sliding heat generation is reduced by the cooling action of the oil jet to the inner diameter side of the seal runner, thereby improving the durability. It is an object of the present invention to provide a rotary shaft sealing device that can be increased and widened in application range.

[0020]

In order to achieve the above object, a first aspect of the present invention comprises a housing provided on a fixed portion and a cylindrical seal runner provided on a rotary shaft and rotating integrally. A plurality of circumferentially divided seal rings located on the outer peripheral surface of the seal runner, a cover ring provided on the outer peripheral surface of the seal ring, and the cover ring and the seal ring inside the housing. A seal ring kit having a biasing member that biases the seal ring toward the end surface of the seal ring, and between the inner peripheral surface of the seal ring and the outer peripheral surface of the seal runner. In the rotary shaft sealing device that seals between the fixed portion and the rotary shaft,
A rotary shaft sealing device is characterized in that the cylindrical seal runner is formed by alternately and continuously forming thick portions and thin portions.

A second aspect of the present invention includes a housing provided in the fixed portion and a cylindrical seal runner provided on the rotary shaft and rotating integrally with the housing. The outer peripheral surface of the seal runner is provided in the housing. A seal ring having a plurality of circumferentially divided seal rings, a cover ring provided on the outer peripheral surface of the seal ring, and a biasing member that biases the cover ring and the seal ring inward. A kit is provided to seal between the fixed portion and the rotating shaft by sealing between the housing and the end surface of the seal ring and between the inner peripheral surface of the seal ring and the outer peripheral surface of the seal runner. In the rotating shaft seal device configured as described above, the tubular seal runner is formed by alternately and continuously forming a thick portion and a thin portion, and further, an oil jet is provided inside the seal runner. It was adapted to morphism is obtained by constituting the rotary shaft seal device according to claim.

Further, in any of the inventions, the thickness between the thick portion and the thin portion of the seal runner is gently changed, the seal runner is formed in a thick cylindrical shape, and A means for forming holes at predetermined intervals, forming a thick portion between each hole, and forming a thin portion at the outer peripheral portion forming each hole is adopted. The direction of the part is 0 ° to ± 85 ° with respect to the axial direction of the rotating shaft.
It is in the range of.

[0023]

According to the present invention, the above means are adopted.
When the rotary shaft starts rotating, the seal runner also starts rotating integrally. Since the seal runner is formed by alternately and continuously forming thick and thin portions, centrifugal force acts on the thick portion having a large mass during rotation, and the thick portion expands outward. As a result, a wedge-shaped gap is generated between the outer peripheral surface of the thin portion and the inner peripheral surface of the seal ring, and the outer peripheral surface of the thick portion slides on the inner peripheral surface of the seal ring. Becomes more significant as the rotation axis becomes faster. Therefore, when the rotating shaft rotates at a high speed, the sliding portion becomes smaller, so that the sliding heat generation amount is reduced so that the thermal limit of the sliding material is not exceeded and the durability is improved.

When the rotary shaft starts rotating, the seal runner also starts rotating integrally. Since the seal runner is formed by alternately and continuously forming thick and thin portions, centrifugal force acts on the thick portion having a large mass during rotation, and the thick portion expands outward. As a result, a wedge-shaped gap is generated between the outer peripheral surface of the thin portion and the inner peripheral surface of the seal ring, and the outer peripheral surface of the thick portion slides on the inner peripheral surface of the seal ring. Becomes more significant as the rotation axis becomes faster. Therefore,
When the rotating shaft rotates at high speed, the sliding part becomes smaller and the sliding heat value decreases, so that the thermal limit of the sliding material is not exceeded. In addition to the small amount, the effect of sliding heat generation is reduced by the cooling action of the oil jet to the inner diameter side of the seal runner, whereby the durability can be improved and the applicable range can be widened.

Further, by smoothly changing the thickness between the thick and thin portions of the seal runner, the wedge-shaped gap can be made larger than in the case where it does not change gently, and the seal runner can be made thicker. By forming it in a tubular shape, providing holes at predetermined intervals in the circumferential direction, forming a thick part between each hole, and forming a thin part at the outer peripheral part forming each hole, An oil jet can be injected inside the hole to prevent oil from scattering. Further, if the direction of the thick portion and the thin portion is within a range of 0 ° to ± 85 ° with respect to the axial direction of the rotating shaft, centrifugal force acts on the thick portion when the seal runner is rotated by the rotation of the rotating shaft. The thick portion can bulge outward due to the action of.

[0026]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of the present invention shown in the drawings will be described below. FIG. 1 shows a rotary shaft seal device 1 according to the present invention.
A schematic cross-sectional view of the above is shown, and a seal runner 4 is integrally fixed to the outside of the rotary shaft 2 via a sleeve 3.

In the housing 5 fixed to the fixed portion X with a predetermined distance from the rotary shaft 2, a seal ring 6 surrounding the outside of the seal runner 4 and the seal ring 6 are provided.
The cover ring 7 that surrounds the outside of the
Seal ring kit 9 including an annular extension spring 8 for urging the seal ring inward and a key (not shown) for fixing between the seal ring 6 and the cover ring 7.
Is provided. The key of the seal ring kit 9 is fixed to the housing 5 by a rotation lock pin (not shown).

The seal ring 6 is a ring divided into two or more parts in the circumferential direction, and is held in contact with the outer peripheral surface of the seal runner 4 attached to the rotary shaft 2 with the same curvature. The cover ring 7 is a ring divided into two or more parts in the circumferential direction, and is held in contact with the outer peripheral surface of the seal ring 6 with the same curvature. On the inner peripheral surface of the seal ring 6, there are provided a plurality of grooves 6a extending in the axial direction while leaving a part on the side in contact with the housing 5, and a groove 6b in the circumferential direction that connects the grooves 6a on the housing 5 side. (See Figure 10). Similarly, a groove 6c is also provided on the housing side surface of the seal ring 6.

The divided portion of the seal ring 6 has a step-divided structure to eliminate a gap in the axial direction. That is, when the seal ring 6 is set on the outer peripheral portion of the seal runner 4, the gap a widens in the circumferential direction in the divided portion (see FIG. 10). Note that, in FIG. 10, the gap a is shown to be larger than that in the state in which it is set on the outer peripheral portion of the seal runner 4.

The cover ring 7 is located on the outer periphery of the seal ring 6 and covers the divided portion of the seal ring 6 in a state where the phase of the divided portion is shifted in the circumferential direction so as to close the gap a.

Since the seal ring 6 and the cover ring 7 are divided in the circumferential direction, the dimensions of the seal ring 6 and the cover ring 7 can be tracked with respect to the shaft, and further sliding displacement and wear can be tracked. Then, it is possible to always slide on the shaft or follow the seal through a minute fluid film. The follow-up amount due to wear (wear allowance) depends on the gap a of the divided portion.

The compression spring 10 axially presses the seal ring kit 9 through the plate 11 to press the end surface of the seal ring 6 against the housing 5,
Add the necessary seal load at the initial stage.

The extension spring 8 is mounted on the rotary shaft 2 by pressing the seal ring 6, the cover ring 7 and the key in the radial direction, and in this state, applies a necessary seal load to the sliding portion in the initial stage. .

Reference numeral 13 is a spring retainer for holding the compression spring 10, and 12 is a snap ring for holding the spring retainer 13 in the housing 5.

Further, the thickness of the portion of the seal runner 4 that slides on the seal ring 6 is not constant, and
As shown in, the thick portions 4a and the thin portions 4b are alternately and continuously formed. 2 is a schematic sectional view of the seal runner 4, FIG. 3 is a perspective view, and FIG. 4 is a view taken along the line C-C of FIG. The number of the thick portions 4a and the thin portions 4b 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 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 seal runner 4 integrally fixed to the rotary shaft 2 by the sleeve 3 also rotate.

The outer peripheral surface of the seal runner 4 is in sliding contact with the inner peripheral surface of the seal ring 6, and the sliding effect exerts a sealing effect. That is, the acting differential pressure is sealed by the seal dams 45 and 46 of the seal ring 6. The seal dam 45 is the seal runner 4.
The seal dam 46 is for sealing with the housing 5, and the seal dam 46 is for sealing with the housing 5. Also, P1 is the high pressure side of the gas chamber,
P2 is a bearing chamber.

The seal dams 45 and 46 of the seal ring 6 have a very narrow structure by forming the pressure balancing grooves 6a, 6b and 6c as described above in order to reduce the fluid force due to the differential pressure. ing. When the differential pressure is small, the pressure balancing grooves 6a, 6b, 6c provided on the inner peripheral surface or the end surface of the seal ring are not necessary, and the seal ring 6 is formed on a flat inner peripheral surface without grooves.

In the conventional rotary shaft seal device 31, since the seal runner 34 has a uniform thickness, the seal runner 34 is deformed in a direction in which it expands due to centrifugal force when the number of rotations increases. Therefore, the contact surface pressure with the seal ring 36 becomes large and heat is generated, and when the material of the sliding runner of the seal runner 34 and the seal ring 36 exceeds the thermal limit, it is rapidly worn and the sealing effect cannot be exhibited. .

However, in the rotary shaft seal device 1 according to the present invention, the shape of the seal runner 4 is the thick portion 4
Since the portions a and the thin portions 4b are provided alternately, the thick portions 4b having a large mass do not swell evenly and are largely swelled and deformed as shown in FIG.

Therefore, the gap A between the thin portion 4b of the outer peripheral surface of the seal runner 4 and the inner peripheral surface of the seal ring 6 has a wedge shape, and the front half portion which gradually increases toward the rear in the rotational direction of the seal runner 4. It is formed by A1 and the latter half A2 which becomes smaller gradually. Then, a dynamic pressure effect as shown in FIG. 5 occurs on the thick portion 4a side of the latter half portion A2, and the sliding load of the seal ring 6 is reduced by this dynamic pressure effect, so that the thermal limit of the material is exceeded. It is possible to prevent the sudden wear.

The first half A1 of the gap A is the second half A
Although a dynamic pressure in the opposite direction to 2 is generated, this dynamic pressure has a theoretical maximum pressure of vacuum (actually, it is a much smaller dynamic pressure), and since it does not exceed this, it is in the high speed rotation range. The dynamic pressure on the buoyant side of the centrifugal force will be obtained in a state of prevailing.

Further, the temperature of the sliding portion of the seal rises due to heat generation, and this heat is also transmitted to the seal runner 4 side to deform the seal runner 4. In order to prevent this deformation, cooling is performed by the oil jet 14. Due to this cooling, the thin portion 4b of the seal runner 4 becomes the thick portion 4a.
Since it is cooled more effectively, it contracts from the thick portion 4a, and the gap A is also maintained in a wedge shape.

As described above, the dynamic pressure action obtained from the wedge-shaped clearance A obtained by the deformation of the seal runner 4 is
It is possible to suppress an increase in the sliding load between the seal ring 4 and the seal runner 6 and to broaden the range of application.

Further, by changing the size or the number of the thick-walled portions 4a and thin-walled portions 4b of the seal runner 4, it is possible to adjust the optimum dynamic pressure for the application condition of the seal.

FIG. 6 is a sectional view showing another embodiment of the seal runner 4. What is shown in this embodiment is different from the above-mentioned embodiment in that the thick portion 4a and the thin portion 4b are gently changed.

Even with this seal runner 4, since a wedge-shaped gap is formed between the seal runner 4 and the seal ring 6 during rotation, the range of application can be greatly expanded.

FIG. 7 is a sectional view showing still another embodiment of the seal runner 4. In the structure shown in this embodiment, a plurality of holes 20 extending in the axial direction are provided in the thick seal runner 4 at predetermined intervals in the circumferential direction, and the thick portions 4a are provided between the holes 20.
The thin portion 4b is formed at the outer peripheral portion of the hole 20.

In this seal runner 4, since the cooling fluid flows through the inside of each hole 20, the hole 2 of the seal runner 4
Since the outer diameter portion of the zero portion is the thin portion 4b, it changes during rotation and a wedge-shaped gap is formed between the seal ring 6 and the seal ring 6.

As the shape of the seal runner which obtains the dynamic pressure effect as described above, the thick portion 4a and the thin portion 4b shown in FIGS.
Also, the hole 20 through which the cooling fluid passes in FIG. 8 may be provided so as to be inclined from the state in which it is oriented in the axial direction as long as it is within a range in which the centrifugal force effectively acts. That is, as shown in FIG. 8 which is an arrow view of FIG. 1, the centrifugal force is effective even when the axial direction is set to 0 ° and the angle θ is formed within a range of ± 85 ° from this.

[0051]

In the rotary shaft seal device according to the present invention, only the outer surface of the thick-walled portion of the seal runner having a large mass slides on the seal ring due to the centrifugal force generated by the rotation, so that sliding heat is generated. The amount is reduced, which allows the thermal limits of the material not to be exceeded, preventing wear and increasing durability. In addition, the centrifugal force generated by rotation reduces the sliding area between the seal runner and the seal ring to reduce the amount of heat generated by sliding, and the oil jet is injected to the inner diameter side of the seal runner for cooling. By applying this, the influence of sliding heat generation can be further reduced, and as a result, the durability of the sealing device can be improved and the application range can be widened.

Further, by smoothly changing the thickness between the thick and thin portions of the seal runner, the wedge-shaped gap can be made larger than that in the case where the clearance does not smoothly change, and the optimum dynamic pressure effect can be obtained. Can be set to. By providing a hole inside the seal runner, it is possible to inject an oil jet into the hole to prevent the oil from scattering. If the direction of the thick portion and the thin portion is in the range of 0 ° to ± 85 ° with respect to the axial direction of the rotating shaft, centrifugal force acts on the thick portion when the seal runner is rotated by the rotation of the rotating shaft. 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 seal runner, it is possible to install the conventional seal device only by changing the seal runner. Have an effect.

[Brief description of the drawings]

FIG. 1 is a schematic sectional view showing an entire rotary shaft sealing device of the present invention.

FIG. 2 is a schematic sectional view of a seal runner.

FIG. 3 is a perspective view of a seal runner.

FIG. 4 is a view taken along the line CC of FIG.

FIG. 5 is a schematic cross-sectional view showing deformation of the seal runner during rotation.

FIG. 6 is a partial schematic cross-sectional view showing another embodiment of the seal runner.

FIG. 7 is a partial schematic cross-sectional view showing still another embodiment of the seal runner.

FIG. 8 is a schematic view showing a state where the inner peripheral surface of the seal runner is expanded.

FIG. 9 is a schematic sectional view showing a conventional rotary shaft sealing device.

FIG. 10 is a schematic sectional view showing an inner peripheral surface of a divided portion of the seal ring used in the present invention and the conventional one.

[Explanation of symbols]

 1, 31 ...... Rotary shaft sealing device 2, 32 ...... Rotary shaft 3, 33 ...... Sleeve 4, 34 ...... Seal runner 4a ...... Thick portion 4b ...... Thin portion 5,35 ...... Housing 6, 36 ... ... Seal ring 6a, 6b, 6c, 36a, 36b, 36c ... Groove 7, 37 ... Cover ring 8, 38 ... Extension spring 9, 39 ... Seal ring kit 10, 40 ... Compression spring 11, 41 ...... Plate 12, 42 ...... Snap ring 13, 43 ...... Spring retainer 14, 44 ...... Oil jet 20 ...... Hole 45, 46 ...... Seal dam X ...... Fixed part A ...... Wedge-shaped gap A1 ...... Gap First half of A2 …… Last half of gap P1 …… Gas chamber P2 …… Bearing chamber a …… Gap

Claims (5)

[Claims] 1. A housing (5) provided on a fixed portion (X), and a cylindrical seal runner (4) provided on a rotating shaft (2) and rotating integrally, the housing (5). ), A plurality of circumferentially divided seal rings (6) located on the outer peripheral surface of the seal runner (4), and a cover ring (7) provided on the outer peripheral surface of the seal ring (6), A seal ring kit (9) having the cover ring (7) and a biasing member (8) for biasing the seal ring (6) inward is provided, and the housing (5) and the end faces of the seal ring (6) are provided. And between the inner peripheral surface of the seal ring (6) and the outer peripheral surface of the seal runner (4) to seal between the fixed portion (X) and the rotary shaft (2). In the rotary shaft seal device (1) adapted to The seal runner (4) is formed by alternately and continuously forming thick portions (4a) and thin portions (4b). 2. A housing (5) provided on the fixed portion (X), and a cylindrical seal runner (4) provided on the rotary shaft (2) and rotating integrally, the housing (5). ), A plurality of circumferentially divided seal rings (6) located on the outer peripheral surface of the seal runner (4), and a cover ring (7) provided on the outer peripheral surface of the seal ring (6), A seal ring kit (9) having the cover ring (7) and a biasing member (8) for biasing the seal ring (6) inward is provided, and the housing (5) and the end faces of the seal ring (6) are provided. And between the inner peripheral surface of the seal ring (6) and the outer peripheral surface of the seal runner (4) to seal between the fixed portion (X) and the rotary shaft (2). In the rotary shaft seal device (1) adapted to The thickened portion (4a) and the thinned portion (4b) of the seal runner (4) are alternately and continuously formed, and the oil jet (14) is injected into the seal runner (4). A rotary shaft sealing device characterized in that 3. The thick portion (4) of the seal runner (4)
3. The rotary shaft seal device according to claim 1, wherein there is a gentle change between a) and the thin portion (4b). 4. The seal runner (4) is formed in a thick cylindrical shape, and holes (20) are provided at predetermined intervals in the circumferential direction, and the thickness between the holes (20) is increased. Division (4
3. The rotary shaft seal device according to claim 1, wherein a) has a thin portion (4b) formed at an outer peripheral portion forming each hole (20). 5. The direction of the thick portion (4a) and the thin portion (4b) is 0 ° to ±± with respect to the axial direction of the rotating shaft (2).
The rotary shaft seal device according to claim 1, wherein the rotary shaft seal device has an angle of 85 °.