JPS5920040B2 - Sealing device for rolls - Google Patents

Description

[Detailed description of the invention] A cylindrical shell is rotatably attached to a fixed shaft that is concentrically inserted through the cylindrical shell as a roll for applying pressure treatment such as rolling or calendering to a strip-shaped product such as paper. Alternatively, the shell can be forcedly rotated by interlocking with an appropriate power mechanism, and a pressurized chamber is formed between the inner circumferential surface of the shell and the outer circumferential surface of the shaft, into which a pressure medium, that is, oil, is pressurized. However, it is known that both ends of the pressurizing chamber in the axial direction are shielded and sealed by a sealing device, but the present invention
The present invention relates to an improvement of the sealing device in the roll configured as described above.

According to this type of roll, by adjusting the hydraulic pressure in the pressurizing chamber appropriately according to the degree of pressure received by the roll during pressure treatment of the strip-shaped article, this is applied to the shell portion facing the pressurizing chamber, that is, the strip-shaped article. The pressure-receiving part, which is normally subjected to pressure treatment by being pinched between rolls, can be held flat without causing concave deflections due to the pressure-receiving action of the pressure treatment, and can also be held in a convex shape as necessary. This allows the strip to be bulged and deformed, thereby ensuring that the pressure treatment of the strip is always performed satisfactorily depending on the processing conditions.

Therefore, for this type of roll, the important point is how to configure the sealing device to secure the pressurized chamber. Conventional sealing devices of this type are generally as shown in Fig. 1. As shown in FIG. 1, grooves 4 are formed on the shaft 1 side at both axial ends (FIG. 1 shows one end side) of the pressurizing chamber 6, and the grooves 4 open toward the seal receiving surface 3 formed on the shell 2 side. , a seal body 5 is slidably inserted and supported in the opening of the groove 4 in a direction perpendicular to the seal receiving surface 3, that is, in the axial direction;
A communication path 7 is formed to communicate from the pressurizing chamber 6 to the groove 4 which is closed by the seal body 5, and further inside the groove 4,
A compression coil spring 8 is disposed, and the seal body 5 is brought into pressure contact with the seal receiving surface 3 by the spring 8.

By the way, in the roll, as the pressure received by the roll increases due to pressure treatment, the pressure in the pressurizing chamber 6 is increased accordingly, so that the sealing force by the sealing device, that is, the sealing force on the seal receiving surface 3 of the seal body 5 is increased accordingly. Although it is necessary to make the pressure contact force more uniform, according to the sealing device configured as described above, when hydraulic pressure is applied to the pressurizing chamber 6, this hydraulic pressure flows into the groove 4 through the communication path 7. also acts on the spring 8
As a result, the pressed seal body 5 is pressed against the seal receiving surface 3 more strongly, and therefore, the higher the oil pressure in the pressurizing chamber 6, the more the seal body 5 is pressed against the seal receiving surface 3. Since the force, that is, the sealing force increases, a sealing effect corresponding to the oil pressure in the pressurizing chamber 6 can be expected.

However, if the hydraulic pressure in the pressurizing chamber 6 is made to directly act as a pressing force on the seal receiving surface 3 of the seal body 5, there will be few problems if the pressure in the pressurizing chamber 6 is not very high. When the pressure is high, the pressing force becomes larger than necessary, causing various problems.

In other words, if the pressing force of the seal body 5 against the seal receiving surface 3 becomes larger than necessary, the portion of the seal body 5 that is in pressure contact with the seal receiving surface 3 will become severely worn, and during long-term use,
There is a risk that the portion of the seal body 5 will become larger and wear out, and that the seal body 5 will eventually be displaced to a state where it cannot reliably receive the suppressing action of the spring 8.

In such a state, when the pressurization of oil into the pressurizing chamber 6 is stopped, the seal body 5 is not pressed against the seal receiving surface 3 by the spring 8 and is in a free state, so that the pressurizing chamber When hydraulic pressure is applied to 6 again, oil leaks from the pressurized chamber 6 between the seal body 5 and the seal receiving surface 3,
A sealing action can no longer take place.

Furthermore, as the pressure force of the seal body 5 against the seal receiving surface 3 increases, the lubricating action between the seal body 5 and the seal receiving surface 3 cannot be performed well, and together with this, the shell 2 The seal body 5 greatly impedes the smooth rotation of the rotor.

If such a braking phenomenon occurs, not only will good pressure processing not be carried out, but when the shell 2 is forcibly rotated by the power mechanism, an unnecessarily overload will be applied to the power mechanism, which may cause a failure. Become.

Moreover, due to the strong contact between the seal body 5 and the seal receiving surface 3, high heat is likely to be generated in the contact area, and this heat generation phenomenon deteriorates properties such as the viscosity of the oil, further reducing the above-mentioned lubricating effect. Abrasion of the seal body 5 and occurrence of a braking phenomenon of the shell 2 are promoted.

Further, the above-mentioned problems are likely to occur even when the pressure inside the pressurizing chamber 6 is not set to high pressure and when the shell 2 is rotated at high speed.

Therefore, the roll equipped with the conventional sealing device described above cannot be used as a roll that requires high pressure in the pressurizing chamber 6 and pressure treatment, such as a roll for rolling steel or aluminum with large rolling blades. The reality is that the shell 2 cannot be rotated at high speed to speed up the pressure treatment, and its range of use is severely limited.

In view of the above points, the present invention provides an improved sealing device that can perform a good sealing action over a long period of time even when the pressure chamber is set at high pressure or when the shell is rotated at high speed. This is intended to ensure that the pressure treatment of the strip-shaped article by the rolls can always be performed satisfactorily and quickly.

Hereinafter, one embodiment will be specifically described with reference to FIGS. 2 to 5.

In the figure, 11 is a roll, and this roll 11' has a cylindrical iron shell 12 made of a desired material as shown in FIGS.
a and an iron shaft 13 formed into a stepped shaft shape having both end support parts 13b and 13b of smaller diameter are inserted concentrically, and the shell 120 both end parts 12b and 12b are connected to the shaft 130 both end support parts. 13b, 13b through bearings 14.degree. 14 to support the shaft 130 rotatably and immovably in the axial direction, and the shaft 130 both end support portions 13b.

13b is fixedly supported 15, 15 to form a cylindrical intermediate chamber 16 between the inner circumferential surface 12a of the shell 12 and the outer circumferential surface of the shaft 13. A pair of sealing devices 17°17 capable of shielding and sealing the intermediate chamber 16 along the axial direction of the roll 11 are disposed at a portion approximately equally divided into two vertically.
7 divides the intermediate chamber 16 into two approximately semi-cylindrical upper and lower chambers, and furthermore, at both ends in the axial direction of the upper intermediate chamber 16,
A pair of sealing devices 18 and 18 capable of shielding and sealing this are provided, and the upper intermediate chamber 16 is hermetically sealed by each of the sealing devices 17 and 18 regardless of the shell 120 rotations, and the shaft 13 is sealed. An appropriate number of oil supply passages 19° 19 are connected to an appropriate oil supply mechanism (not shown) and communicated with the upper intermediate chamber 16, and are connected to an appropriate oil drainage mechanism (not shown). An appropriate number of oil drain passages 20, 20 are formed to connect and communicate with the lower intermediate chamber 16, and the upper intermediate chamber 16 is supplied with oil as a pressure medium at an appropriate pressure by the oil feeding mechanism. The pressurizing chamber 16a is press-fitted into the pressurizing chamber 16a, and the lower intermediate chamber 16 is formed into an oil draining chamber 16b from which oil can be drained to the oil draining mechanism.

Each of the sealing devices 18 for shielding and sealing the axial end portion of the pressurizing chamber 16a along its circumferential direction is configured as follows according to the present invention.

That is, in this embodiment, as shown in FIGS. 2 and 4, an annular ring is located at the axial end of the intermediate chamber 16 and is provided at the end 12b of the shell 12, which also serves as a bearing 14 receiver. The seal receiver 21 is fitted and fixed to the body end face 13C of the shaft 13 so as to face it, and the annular seal holder 22 is fixed to the body end face 13c of the shaft 13 so as to face the seal receiver 21. The end face of the seal receiver 21 facing the end face of the seal holder 22 is a seal receiving surface 21a.

The body end surface 13c side of the shaft, that is, the seal holder 2
A groove 23 extending in a trapezoidal shape along the circumferential direction of the pressurizing chamber 16a is formed in the end face of the pressurizing chamber 16a, and a support body extending in the longitudinal direction and having a uniform U-shaped longitudinal section is formed in the groove 23. 24 is fitted with its opening protruding an appropriate amount from the end face of the seal holder 22 and directly facing the seal receiving surface 21a, and is fixed by appropriate means, thereby forming the inside of the seal holder 24 with the first pressure chamber 25. None, at the opening of the first pressure chamber 25, that is, at the opening end of the support body 24, a seal body 26 extending in the longitudinal direction and having a uniform U-shaped vertical cross section is provided with the opening end 26a as a seal receiving surface. 21a, preferably in the axial direction, that is, the seal receiving surface 2
It is fitted and supported so as to be slidable in a direction substantially perpendicular to 1a.

The inside of the seal body 26 has a seal receiving surface 21a.
Therefore, the second pressure chamber 27 is closed, and the first pressure chamber 27 is closed.
The end surface of the seal body 26 facing the pressure chamber 25, that is, the outer end surface 26 of the rear wall of the seal body 26 that closes the first pressure chamber 25.
A first pressure-receiving surface obtained by projecting b onto a surface perpendicular to the sliding direction of the seal body 24 is a second pressure-receiving surface obtained by transmissively projecting the second pressure chamber 27 onto a surface perpendicular to the sliding direction. It is configured to have an appropriately larger area than the surface.

Therefore, when the same hydraulic pressure is applied to both pressure chambers 25 and 27, the seal body 26 is pressed against the seal receiving surface 21a in the direction of its sliding force by the entire pressure applied to the first pressure receiving surface. On the other hand, since the second pressure receiving surface tends to be separated from the seal receiving surface 21a by the total pressure applied to it, the total pressure acting on the area corresponding to the area difference between the first pressure receiving surface and the second pressure receiving surface ends up being It is adapted to be brought into contact with the seal receiving surface 21a by pressure.

In this embodiment, the support body 24 forming the first pressure chamber 25 and the seal body 26 forming the second pressure chamber 27 are both configured in a U-shape with a uniform cross section. The pressure receiving surface is aligned with the outer end surface 26b of the rear wall of the seal body 26, and the second pressure receiving surface is aligned with the inner end surface 26c of the rear wall, and the difference in area is equal to the sum of the longitudinal cross-sectional areas of the upper and lower walls of the seal body 26. corresponds to

The seal receiver 21 is made of the above-mentioned iron like the shell 12, the support body 24 is made of a metal with excellent strength, such as steel, and the seal body 26 is made of iron as described above. It is formed of a metal softer than the iron seal receiver 21, such as copper, brass, bronze, or oilless metal.

Further, a first communication passage 28 is formed on the circumferential surface of the seal holder 220 to communicate from the pressurizing chamber 16a to the first pressure chamber 25 by penetrating the earthen wall portion of the support 24. A second communication passage 29 is formed in the rear wall of the body 26 to communicate from the first pressure chamber 25 to the second pressure chamber 27. It communicates with the pressurizing chamber 16a via the pressure chamber 25.

The communicating passages 28, 29 are formed one or more as desired with a desired size and shape.

Therefore, when hydraulic pressure is applied to the pressurizing chamber 16a, the same hydraulic pressure is applied to both the pressure chambers 25 and 27.

Note that the first communication path 28 is formed at a position where the seal body 26
It is located so that it cannot be blocked by an earthen wall.

In addition, an appropriate number of compression coil springs 30 are provided in the first pressure chamber 25.
(only the minus sign is shown) is provided internally, and this spring 30 urges the seal body 26 into pressure contact with the seal receiving surface 21a.

Note that each of the sealing devices 18, that is, its constituent parts, such as the groove 23, the support body 24, and the sealing body 26, are connected to the pressurizing chamber 16a.
In order to shield and seal the ends in the axial direction, the grooves are extended in a trapezoidal shape as shown in FIG. Of course, it may be extended.

Further, in this embodiment, in particular, each sealing device 17 for shielding and sealing the circumferential end of the pressurizing chamber 16a in the axial direction has the same structure as the sealing device 18.

That is, as shown in FIGS. 3 and 5, the shaft 13
A groove 31 is formed in the outer peripheral surface of the shell 12 in the axial direction, and a support 32 having a uniform U-shaped vertical cross section is formed in the groove 31, and its opening is formed in the inner peripheral surface 12a of the shell 12. They are fitted and fixed in a state where they face directly, and the inside thereof becomes a first pressure chamber 33,
At the opening of the first pressure chamber 33, a sealing body 34 having a uniform U-shaped vertical cross section is provided with its opening end facing toward the shell inner peripheral surface 12a.
It is fitted and supported so as to be slidable in the radial direction of the shell 12 (preferably in the axial direction, that is, in the direction perpendicular to the shell inner circumferential surface 12aK) while being in contact with the shell 12a.

Further, a first communication passage 36 that passes through the support body 32 from the pressurizing chamber 16a and communicates with the first pressure chamber 33, and a first communication passage 36 that passes through the rear wall of the seal body 34 from the first pressure chamber 33 and communicates with the seal body 3
A second communication passage 37 is formed in each of the pressure chambers 4 to communicate with a second pressure chamber 35 in the pressure chamber 4.

One or more communication passages 36, 37 are formed in the axial direction to have a desired size and shape.

Further, an appropriate number of compression coil springs 38 (only the negative one is shown) are disposed in the first pressure chamber 33 to urge the seal body 34 into pressure contact with the shell inner circumferential surface 12a.

Note that each sealing device 17 is sealingly connected to each of the sealing devices 18 as in the usual case.

Further, the support body 32 and the seal body 34 and the seal body 26 are respectively molded from the same material.

Next, the sealing action of the sealing device 18 will be explained with reference to the above embodiment. When no hydraulic pressure is applied to the pressurizing chamber 16a, the open end 26a of the sealing body 26 is brought into pressure contact with the seal receiving surface 21a by the spring 30. It is being

From this state, when hydraulic pressure is applied to the pressurizing chamber 16a, the oil in the pressurizing chamber 16a is transferred from the first communication path 28 to the first pressure chamber 2.
5 and further into the second pressure chamber 27 from the second communication passage 29, and the respective chambers 16a.

The same hydraulic pressure acts on 25 and 27, respectively.

At this time, the seal body 26, which is capable of sliding displacement, is subjected to a pressing force in the direction toward the seal receiving surface 21a due to the total pressure acting on the outer peripheral surface 26b of the rear wall, that is, the first pressure receiving surface 26b. On the other hand, due to the total pressure acting on the inner end surface 26c of the rear wall, that is, the second pressure receiving surface 26e, the seal receiving surface 2
A non-pressing force is applied in a direction away from 1a.

However, the first pressure receiving surface 26b has a larger area than the second pressure receiving surface 26c, and each pressure receiving surface 26b, 26
Since the oil pressures acting on c, that is, the pressure per unit area, are equal, the seal body 26 is pressed against the seal receiving surface 21a with a force obtained by subtracting the non-pressing force from the pressing force.

That is, the seal body 26 acts as if it were the first pressure receiving surface 26b.
The seal receiving surface 21a receives the oil pressure of the pressurizing chamber 16a on the pressure receiving surface having an area obtained by subtracting the area of the second pressure receiving surface 26c from the area of the seal receiving surface 21a.
It will be pushed to.

Therefore, even when the pressurizing chamber 16a is under high pressure, by appropriately setting the difference in area between the first pressure receiving surface 26b and the second pressure receiving surface 26c, the opening end 26a of the seal body 26 can be adjusted to the seal receiving surface. A good sealing action can be performed over a long period of time without being pressed against the surface 21a more strongly than necessary, and without causing the problems mentioned at the beginning.

Further, the seal body 26 is slidable in a direction substantially perpendicular to the seal receiving surface 21a, and the direction in which the seal body 26 is pressed against the seal receiving surface 21a coincides with the pressing direction by the spring 30, and the above-mentioned conditions are satisfied. Even if the portion of the seal body 26 that is in pressure contact with the seal receiving surface 21a is accidentally worn out, the amount of wear is extremely small, so when the pressurization of hydraulic pressure into the pressurizing chamber 16a is stopped, the seal body 26 will continue to wear even after wear occurs. is held by spring 30.
The contact surface 21 is securely pressed against the receiving surface 21.

That is, unlike the conventional structure mentioned at the beginning, the seal body 26 is not significantly displaced outside the pressing area of the spring 30 due to wear.

Due to the above seal structure, the seal body is worn out and the seal body 2
6 is displaced, the state of pressure contact between the seal body 26 and the seal receiving surface 21a does not change, and the sealing effect can be kept constant. Of course, the lubricating oil, that is, the drain oil accumulated in the oil drain chamber 16b is discharged from the oil drain path 20.

Therefore, according to the seal device 18 according to the present invention, the first pressure receiving surface (seal By appropriately setting the area difference between the outer end surface 26b of the rear wall of the body 26 and the second pressure receiving surface (the inner end surface 26c of the rear wall), an appropriate sealing force can be generated by the seal body 26. , and can be designed in this way very easily.

Furthermore, since the pressing force of the seal body 26 against the seal receiving surface 21a does not become larger than necessary, the shell 12 can be rotated at high speed while maintaining a good sealing effect.

As can be understood from the above points, the roll 11 equipped with the sealing device 18 according to the present invention is a calender roll, a press roll, a wire heart fresto roll, etc. for paper manufacturing that keeps the pressure chamber 16a at a relatively low pressure. It goes without saying that it can be used as a back-up roll or work roll for rolling steel, aluminum, etc. with large rolling blades and skin passes that require the pressure chamber 16a to be kept at high pressure, which could not withstand use in the past. In addition, the shell 12 can be rotated at high speed to speed up the pressure treatment.

In addition, in the above embodiment, one! Since the sealing device 1T that shields and seals the circumferential end of the pressurizing chamber 16a is also configured to obtain the same sealing effect as the sealing device 18, the above-mentioned advantages of the roll 11 become even more remarkable.

That is, the sealing action by the sealing device 17 is similar to the above-mentioned action, so the details are omitted, but when no hydraulic pressure is applied to the pressurizing chamber 16a, the sealing body 34 closes the inner periphery of the shell with the spring 38. It is pressed against the surface 12a.

When hydraulic pressure is applied to the pressurizing chamber 16a, the same pressure as in the pressurizing chamber 16a acts on the first pressure chamber 33 and the second pressure chamber 35 through the first communication passage 36 and the second communication passage 37. .

Therefore, the seal body 34 is pressed against the inner circumferential surface 12a of the shell 12 with a force obtained by subtracting the total pressure acting on the inner end surface 34b of the rear wall from the total pressure acting on the outer end surface 34a of the rear wall of the seal body 34. Therefore, even when the pressurizing chamber 16a is under high pressure, the seal body 34 remains in contact with the shell inner circumferential surface 12.
A is not pressed more strongly than necessary.

Therefore, according to the sealing device 17, the circumferential end of the pressurizing chamber 16a can be protected for a long period of time without causing various problems such as severe wear of the seal body 34 or interference with smooth rotation of the shell 12. Good shielding and sealing can be achieved over the entire area.

Note that the configuration of the sealing device 18 according to the present invention is not limited to the above-described embodiment, and may be configured as follows, for example, and the same effects as in the above-described embodiment can be achieved.

In the following, for convenience, the same parts as in the above embodiment are given the same reference numerals and a dash.

That is, in the sealing device 18, the first communicating path 2
8 and the second communicating path 29 can be formed at any position.
It is sufficient if the hydraulic pressure in the pressurizing chamber 16a is directly introduced into each pressure chamber 25 and 27.

Furthermore, the configuration of the seal body 24 and the pressure chambers 25 and 27 is arbitrary, and the point is that the first pressure receiving surface may have an appropriately larger area than the second pressure receiving surface. .

Further, each of the sealing devices 18 may be configured to extend in an annular manner so as to shield and seal the axial end portion of the oil drain chamber 16b as well.

Therefore, instead of the sealing device 17 that has such a configuration and seals the intermediate chamber 16 by dividing it into a pressurizing chamber 16a and an oil drain chamber 16b, a sealing device 17' having a configuration as shown in FIG. 6 is used. In this case, the oil drain passage 20 is connected to a second oil feeding mechanism (not shown), and the oil drain chamber 16b is configured as a pressurizing chamber similar to the pressurizing chamber 16a. Can be done.

That is, the sealing device 17' inserts a solid sealing body 34' into the groove 31' formed on the outer peripheral surface of the shaft 13.
The shell 12 is slidably inserted and supported in the radial direction to form a pressure chamber 33' inside the concave groove 31', and is connected to the shaft 13 to a third oil supply mechanism (not shown) to form a pressure chamber. A communication passage 39 is formed to communicate with the pressure chamber 33', and the third oil supply mechanism applies appropriate hydraulic pressure from the communication passage 39 into the pressure chamber 33', thereby causing the seal body 34' to move around the inner periphery of the shell. Surface 12a
It is constructed so that it can be brought into moderate pressure contact with the

With this configuration, for example, the upper pressurizing chamber 16a
Different pressures can be applied to the upper and lower pressurizing chambers 16b, respectively, and the roll 11 can be placed in the middle of a multi-stage roll device as shown in FIG.

For example, the pressure in the upper pressurizing chamber 16a is set to high, the belt-like product 41 is subjected to strong pressure treatment using the uppermost rolls 40 and 11, and the pressure in the lower pressurizing chamber 16b is set to a relatively low pressure. The part of the roll 11 that presses against the lower roll 42, that is, the part of the shell 12 that faces the lower pressurizing chamber 16b, is prevented from being bent in a concave shape, and the roll IL42 is used to prevent the belt-shaped product 4 from being bent in a concave shape.
1 can be performed satisfactorily.

Further, each of the sealing devices 18 can extend in an annular manner as described above to shield and seal the axial end of the intermediate chamber 16, so that the sealing devices 1
7 and 17' can be omitted and all of the intermediate chamber 16 can be constructed as a - pressurizing chamber.

By doing so, the roll 11 can be placed in the middle of the multi-stage roll device, as described above.

In any case, as is clear from the above description, the sealing device for the roll of the present invention is such that the sealing body is attached to the end of the shell in the first pressure chamber formed on the end face side of the body of the shaft. The seal receiver is slidably supported in a direction substantially perpendicular to the seal receiving surface of a seal receiver fixed opposite to the end surface of the body of the seal member, and a second pressure chamber closed by the seal receiving surface is provided on the side of the seal body. the first communication passage and the second pressure chamber.
The seal body facing the first pressure chamber is connected to the pressurizing chamber via the communication passage so that the same pressure is applied to both pressure chambers by applying hydraulic pressure to the pressurizing chamber. A first pressure receiving surface, which is obtained by projecting an end surface of the seal body perpendicular to the sliding force direction of the seal body onto a plane perpendicular to the sliding force direction of the seal body, directs the second pressure chamber in the sliding force direction. When hydraulic pressure is applied to the pressurizing chamber by setting the area to be appropriately larger than the second pressure-receiving surface obtained by transmission projection on a perpendicular surface, the seal body acts on the first pressure-receiving surface. Since it is configured to be brought into pressure contact with the seal receiving body with the pressure obtained by subtracting the total pressure acting on the second pressure receiving surface from the total pressure acting on the second pressure receiving surface, the hydraulic pressure in the pressurizing chamber is controlled as in the conventional sealing device. It goes without saying that the sealing force can be increased or decreased depending on the level of the oil pressure by using the sealing force, and while maintaining such a sealing effect, the area difference between the first pressure receiving surface and the second pressure receiving surface can be adjusted as appropriate. This prevents the pressing force of the seal body against the seal receiving surface from becoming unnecessarily large, not only when the pressure inside the pressurizing chamber is low, but also when the pressure is high.

Therefore, regardless of the oil pressure in the pressurizing chamber and the rotational speed of the shell, the part of the seal body that is in pressure contact with the seal receiving surface will always be severely worn, and the pressure contact action of the seal body will always prevent the smooth rotation of the shell. In addition, high heat is generated at the contact area between the seal body and the seal receiving surface, causing deterioration of the viscosity and other properties of the pressure medium oil. It can perform a good sealing action.

Therefore, the roll equipped with the sealing device of the present invention can be used as a pressure treatment roll for steel, aluminum, etc. with large reduction blades that require a high pressure in the pressurization chamber, and can be used for all types of materials. The pressure treatment of the strip-shaped article can be performed satisfactorily while fully utilizing the functions of the rolls, and the shell can be rotated at high speed to speed up the pressure treatment.

[Brief explanation of the drawing]

FIG. 1 is a vertical sectional side view showing a conventional sealing device (showing the same parts as FIG. 4), and FIGS. 2 to 5 show an embodiment of a roll equipped with a sealing device according to the present invention. Figure 2 is a vertical side view (the cross section is along the line ■-■ in Figure 3), Figure 3 is a vertical front view (the cross section is along the line ■-■ in Figure 2), FIG. 4 is an enlarged view of the main part of FIG. 2, FIG. 5 is an enlarged view of the main part of FIG. 3, and FIG. 6 is an enlarged view similar to FIG. 5 showing another sealing device. FIG. 7 is a schematic diagram showing an example of a roll device using rolls. 11...Roll, 12...Shell, 1
2a...Inner peripheral surface, 12b...End of shell, 13...Shaft, 13a...
Body of the shaft, 13c... end face of the body of the shaft, 16... intermediate chamber, 16a... pressurizing chamber, 16b... oil drain chamber, 18... Seal device, 21... Seal receiver, 21a...
...Seal receiving surface, 25...First pressure chamber, 26.
... Seal body, 26b ... Outer end surface (first
pressure receiving surface), 26c...inner end surface (2 pressure receiving surface), 2
7...Second pressure chamber, 28...first communication passage, 2
9...Second communication path.

Claims (1)

[Claims] 1. A cylindrical shell is rotatably supported by a fixed shaft inserted concentrically through the cylindrical shell, and a pressurized chamber into which a pressure medium is pressurized is formed between the opposing peripheral surfaces of the two. In a roll, a sealing device for shielding and sealing between both body end faces of the shaft and seal surfaces of seal receivers fixed to both ends of the shell opposite to the body end faces with seal bodies, , a first pressure chamber opening toward the seal receiving surface is provided on the end surface side of the body portion of the shaft, and a seal body in contact with the seal receiving surface is placed in the opening of the first pressure chamber on the seal receiving surface. A first pressure chamber is closed by a seal body that is slidably inserted and supported in a substantially orthogonal direction, and a second pressure chamber is formed within the seal body, which is closed by the seal receiving surface; The seal body has a first pressure-receiving surface obtained by projecting onto a surface perpendicular to the sliding force direction of the seal body, which is an end face of the seal body facing the first pressure chamber, and a first pressure receiving surface that is obtained by projecting the second pressure chamber on a surface perpendicular to the sliding force direction of the seal body. The pressure receiving surface is configured to have an appropriately larger area than the second pressure receiving surface obtained by transmission projection onto the surface, and furthermore, the pressurizing chamber is directly connected to the first pressure chamber or the second pressure chamber is and a second communication path that communicates directly or indirectly from the pressurizing chamber to the second pressure chamber through the first pressure chamber. characterized by
Sealing device in rolls.