JPS6038720Y2 - Sealing device for rolls - Google Patents

Description

[Detailed description of the invention] As a roll for applying pressure treatment such as rolling or calendering to paper or other strip-shaped products, a cylindrical shell is rotatably attached to a fixed shaft that is inserted concentrically through the roll. or further, the shell is interlocked with an appropriate power mechanism to enable forcible rotation, and a cylindrical intermediate chamber formed between the inner circumferential surface of the shell and the outer circumferential surface of the shaft, in the circumferential direction, It is known that the roll is divided into two chambers by a sealing device that shields and seals along the axial direction, and one of the intermediate chambers is configured as a pressurized chamber into which a pressure medium, that is, oil is pressurized. relates to an improvement of the sealing device in a roll configured in this manner.

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. As a result, the pressure treatment of the belt-shaped article can always be performed satisfactorily depending on the treatment situation.

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.
The shell 3 is supported by biting in the rotational direction of the shell 3, and the other edge is in contact with the inner circumferential surface 3a of the shell 3, and is arranged in an inclined manner so as to shield the circumferential end of the pressurizing chamber 4. The seal body 1 is pressed and biased in the direction of rotation of the shell 3 by a plate spring 6 fixedly supported via a spacer 5 in a support groove 2b formed on the outer peripheral surface of the shaft 2, and the other end of the seal body 1 is Pressing the edge against the inner peripheral surface 3a of the shell,
It is configured.

However, if the hydraulic pressure in the pressurizing chamber 4 is made to act as it is as a pressing force on the shell inner circumferential surface 3a of the seal body 1, there will be little problem if the pressure in the pressurizing chamber 4 is not very high. However, when the pressure is high, the pressing force becomes larger than necessary, causing various problems.

That is, if the pressing force of the seal body 1 to the shell inner circumferential surface 3a becomes larger than necessary, the portion of the seal body 1 that is in pressure contact with the shell inner circumferential surface 3a will be severely worn, and during long-term use, the above-mentioned There is a possibility that a portion of the seal body 1 will be greatly worn, and the seal body 1 will eventually be displaced to a state in which it cannot reliably receive the pressing action of the leaf spring 6 (the state shown by the chain line).

In such a state, when the injection of oil into the pressurizing chamber 4 is stopped, the seal body 1 is not pressed against the shell inner peripheral surface 3a by the leaf spring 6 and is in a free state.
Therefore, when hydraulic pressure is applied to the pressurizing chamber 4 again, oil leaks from the pressurizing chamber 4 between the seal body 1 and the shell inner peripheral surface 3a, and the sealing action can no longer be performed.

Furthermore, as the pressure force of the seal body 1 against the shell inner circumferential surface 3a increases, the lubrication effect between the seal body 1 and the shell inner circumferential surface 3a cannot be performed well, and together with this, Smooth rotation of the shell 3 is greatly hindered by the seal body 1.

If such a braking phenomenon occurs, not only will good pressure processing not be carried out, but when the shell 3 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 1 and the shell inner circumferential surface 3a, high heat is likely to be generated in the contact area, and this heat generation phenomenon deteriorates the properties such as the viscosity of the oil, further reducing the above-mentioned lubricating effect. , wear of seal body 1 and shell 3
The occurrence of the braking phenomenon is promoted.

Furthermore, the above-mentioned problems are likely to occur even when the pressure inside the pressurizing chamber 4 is not set to high pressure and when the shell 3 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 4 and pressure treatment, such as a rolling roll for steel or aluminum, etc. In addition, the shell cannot be rotated at high speed to speed up the pressure treatment, and the actual situation is that its range of use is greatly 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 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 10.

In the figure, 11 is a roll, and this roll 11 is the second roll.
As shown in FIG. 3 and FIG. 3, an iron shaft 13 having an appropriate minimum diameter than the inner diameter is inserted concentrically into a cylindrical iron shell 12 made of a desired material, and both ends of the shell 12 are connected to the shaft 13. The shaft 13 is supported rotatably and immovably in the axial direction via bearings 14.14, and both ends of the shaft 13 are fixedly supported 15.15, so that the inner circumferential surface 12a of the shell 12 and the outer circumferential surface of the shaft 13 are fixedly supported. A cylindrical intermediate chamber 16 is formed between them, and a suitable part of the intermediate chamber 16 is divided into approximately two equal parts vertically in the circumferential direction.
A sealing device 17 capable of shielding and sealing the intermediate chamber 16 along the axial direction of the roll 11 is provided, and the intermediate chamber 16 is divided into two approximately semi-cylindrical upper and lower chambers by the sealing device 17. Seal devices 18 capable of shielding and sealing the intermediate chamber 16 are provided at both ends in the axial direction of the intermediate chamber 16, and the upper intermediate chamber 16 is separated from each of the seal devices 1-7.18.
Therefore, a suitable number of oil supply passages 1 are formed, which are tightly sealed regardless of the rotation of the shell 12, and which are connected to a suitable oil supply mechanism (not shown) to the shaft 13 and communicate with the upper intermediate chamber 16.
9.19, and an appropriate number of oil drainage passages 20.20 connected to a suitable oil drainage mechanism (not shown) and communicating with the lower intermediate chamber 16, intermediate chamber 1
6 portion into a pressurizing chamber 16a into which oil as a pressure medium is forced into an appropriate pressure by the oil feeding mechanism, and a lower intermediate chamber 16 portion into an oil draining chamber 16 into which oil can be drained to the oil draining mechanism.
b, respectively.

The sealing device 17 for shielding and sealing both circumferential ends of the pressurizing chamber 16a along the axial direction is configured as follows according to the present invention.

That is, as shown in FIGS. 2 and 4, the shaft 13
A pair of grooves 21, 21 extending in the axial direction and opening toward the inner circumferential surface 12a of the shell are formed at an interval of approximately 1800 mm in the circumferential direction on the outer circumferential surface of the shell. , respectively, a plate-shaped seal body 22 extending in the axial direction is attached to the shell 1.
2 in the radial direction (preferably in the axial direction, that is, the inner circumferential surface of the shell 1
It is fitted and supported so as to be slidable in a direction perpendicular to 2a.

As shown in FIG. 4, the side surface or upper surface 22b of the tip of each seal body 22 facing the pressurizing chamber 16a is formed into an inclined surface so that the cross-sectional shape of the tip becomes tapered.

In this embodiment, in particular, the lower surface 22c of the tip of each seal body 22 is also formed into an inclined surface symmetrical to the upper surface 22b.

Each seal body 22 is made of copper, brass, oilless metal, or the like, which is softer than the iron shell 12 described above.

Further, the shaft 13 is provided with a pressing means 35 for pressing the tip of each seal body 22 against the inner circumferential surface 12a of the shell 12 with a predetermined pressure.

That is, this pressing means 35 forms press-fit passages 23.23 in the shaft 13 that communicate with each groove 21 closed by the seal body 22, and also press-fit passages 23.23.
23 is connected to a second oil feeding mechanism (not shown) that is different from the oil feeding mechanism connected to the oil feeding passage 19, and this second oil feeding mechanism allows the press-fit passage to 23, 23 into the concave grooves 21°21 by pressurizing oil at an appropriate pressure, which is a pressure medium different from the pressure medium pressurized into the pressurizing chamber 16a. 22a
The hydraulic pressure acting on the inner circumferential surface 12a of the shell is pressed with a predetermined pressure.

Further, in this embodiment, the sealing device 18 is
In particular, it is structured as follows.

That is, as shown in FIGS. 3 and 5, annular seal receivers 24, 24, which also serve as bearings 14, 14 receivers, are fitted into the shell 12 at both ends of the intermediate chamber 16 in the axial direction. At the same time, it is fixed to the shaft 13,
Annular seal holders 25, 25 are externally fitted and fixed so as to face the seal receivers 24°24.

An arcuate or trapezoidal concave groove 26 is formed in the end surface of each seal holder 25, and a support 27 having a U-shaped longitudinal section is inserted into each groove 26, and its opening is connected to the end surface of the seal receiver 24. In other words, the seal body 28 having a U-shaped vertical cross section is fitted into the opening of each support body 27 so as to be directly opposed to the seal receiving surface 24a and fixed by appropriate means. With the end portion in contact with the seal receiving surface 24a, the seal receiving surface 2
It is fitted and supported so as to be slidable in the direction perpendicular to 4a, that is, in the axial direction.

Furthermore, each of the supports 27 is equipped with an appropriate number of compression coil springs 29, and these springs 29 press each seal body 28 against the seal receiving surface 24a of the seal receiver 24, and the pressurized chamber A communication path 30 that communicates from the support body 16a to the inside of the support body 27, and a communication path 31 that communicates from the inside of the support body 27 to the inside of the seal body 28 are formed.

The communication passages 30, 31 are formed to have one or several appropriate sizes and shapes.

Note that each seal receiver 24 is connected to the shell 12 and each seal body 2.
8 are made of the same material as the seal body 22.

Therefore, according to this sealing device 18, the pressurizing chamber 16
When hydraulic pressure is applied to a, the inside of the support body 27 closed by the seal body 28 and the seal receiving surface 2 of the seal receiving body 24
Since the same hydraulic pressure as the above-mentioned hydraulic pressure acts on the inside of the seal body 28 closed by the seal body 4a, the seal body 28 corresponds to the area difference between the outer end surface 28a and the inner end surface 28b of the rear wall. The seal receiver 24 receives hydraulic pressure on the very small surface.
Although the hydraulic pressure inside the pressurizing chamber 16a is directly utilized,
Even when the pressure inside the pressurizing chamber 16a is high, the sealing body 28
is not pressed against the seal receiving surface 24a more strongly than necessary, and each end of the pressurizing chamber 16a in the axial direction can be well shielded and sealed.

Next, the operation of the sealing device 17 according to the present invention will be explained with reference to the above embodiment.

When applying hydraulic pressure to the pressurizing chamber 16a, the second oil supply mechanism presses oil at a predetermined pressure into the groove 21 from the press-in passage 23, and this hydraulic pressure is applied to the rear end surface 22a of the seal body 22.
is received, and the tip of the seal body 22 touches the shell inner circumferential surface 12a.
The circumferential end of the pressurizing chamber 16a is shielded and sealed.

At this time, since the upper surface 22b of the tip of the seal body 22 is formed into a tapered slope, as shown in FIG.
Due to the hydraulic pressure P in the pressurizing chamber 16a, the tip of the seal body 22 is pressed down and the inner circumferential surface of the shell 1 is pressed down.
A component force P that tries to bite into the shell 2a acts, and a component force P2 that tries to separate the seal body 22 from the shell inner circumferential surface 12a acts.

Therefore, even if the hydraulic pressure acting in the groove 21 is constant, the sealing force by the seal body 22 is
The increase or decrease will be adjusted as appropriate depending on the change in the oil pressure applied to the inside of a.

That is, the present inventor believes that when the oil pressure in the pressurizing chamber 16a is increased, if the upper surface 22b of the seal body 22 is not formed with an inclined surface of the shape described above, the force pushing down the seal body 22 will be too strong. Experimental results showed that the sealing force was greater than necessary, and the sealing body 22 was severely worn, requiring replacement in a short period of time.

Note that the pressing force on the seal body 22 by the pressing means 35, that is, the hydraulic pressure applied in the groove 21, is the hydraulic pressure applied in the pressurizing chamber 16a (if it is necessary to change this hydraulic pressure, the hydraulic pressure to be changed is The angle of inclination of the upper surface 22b of the tip end of the seal body 22 is appropriately set in consideration of the hydraulic pressure applied to the pressurizing chamber 16a and the groove 21.

In this way, if the pressing force applied by the pressing means 35 to the seal body 22 and the inclination angle of the top surface 22b of the tip end of the seal body 22 are set appropriately, the seal can be maintained regardless of the level of oil pressure in the pressurizing chamber 16a. The pressing force of the body 22 against the shell inner circumferential surface 12a, that is, the sealing force, is not insufficient or becomes larger than necessary, and the seal body 22 is severely worn, or the braking phenomenon of the shell 12 or the shell inner circumferential surface 12a is prevented. Problems such as heat generation at the contact portion between the seal body 22 and the seal member 22 are prevented as much as possible, and a good sealing effect can be maintained over a long period of time.

Furthermore, since the seal body 22 is capable of sliding in the radial direction (preferably in the axial direction perpendicular to the shell inner circumferential surface 22a), even when it is unexpectedly worn, only the worn portion is slidable on the shell inner circumference. Since the sealing force is caused to follow the direction of the surface 12a, a decrease in sealing force is prevented, and the sealing state on the shell inner circumferential surface 12a does not change.

As a result, even better sealing action can be expected.

By the way, when hydraulic pressure is applied to the pressurizing chamber 16a, as shown in FIG. 8, the shell 12 and the shaft 13 are relatively flexibly deformed, and the distance between the opposed peripheral surfaces of the two 12 and 13 changes in the axial direction. .

The amount of change in this interval is slight at both end portions of the pressurizing chamber 16a in the axial direction, but becomes considerably large at the central portion in the axial direction.

Therefore, especially along the axial direction, the shell inner peripheral surface 12a
There is a risk that the seal body 22, which needs to be in pressure contact with the axial force, cannot follow the wide change in the distance in the direction of the axial force, resulting in an inconvenience in which the sealing action by the seal body 22 cannot be performed satisfactorily. be.

However, in the sealing device 17 of the embodiment described above, in order to divide the intermediate chamber 16 into approximately two equal parts to form the approximately semi-cylindrical pressurizing chamber 16a, the sealing bodies 22 and 22 are moved approximately 180° in the circumferential direction. Since they are arranged at intervals of , the above-mentioned inconvenience does not occur at all.

That is, when hydraulic pressure is applied to the approximately semi-cylindrical pressurizing chamber 16a, both the above-mentioned 1
2.13 varies greatly in the axial direction (see FIGS. 8 to 10), but at both ends of the pressurizing chamber 16a in the circumferential direction separated by an interval of approximately 180 degrees, the distance shown in FIGS. As is clear from the figure, the spacing hardly changes in the axial direction.

Therefore, the sealing bodies 22, 22 are not required to have great followability, and the sealing action by the sealing device 17 is always performed satisfactorily.

Regarding the sealing device 18, seal receiving surfaces 24 perpendicular to the axial direction formed at both ends of the shell 12 in the axial direction
Since the structure is such that both axial ends of the pressurizing chamber 16a are sealed by bringing the seal bodies 28, 28 into pressure contact with the shell 12 and the shaft 13, the relative relationship between the shell 12 and the shaft 13 is as shown in FIGS. 8 to 10. Even if the seal receiving surfaces 24 a, 24 change as shown in the figure, depending on this, the seal receiving surfaces 24 a, 24
a is naturally not affected, and therefore, the seal bodies 28, 28 are not required to have great followability, and it goes without saying that both ends of the pressurizing chamber 16a in the axial direction are always well sealed.

In addition, the intermediate chamber 16 is divided into approximately two equal parts in the circumferential direction, and the pressurizing chamber 16
Since a is formed into a substantially semi-cylindrical shape, the pressure-receiving area of the shell 12 corresponding to the pressurizing chamber 16a is approximately maximum, and the advantage is that the deformation of this shell 12 by hydraulic pressure can be performed with as small a hydraulic pressure as possible. There is.

Note that the lubricating oil that lubricates between the shell inner circumferential surface 12 a and the seal body 22 and is accumulated in the oil drain chamber 16 b is discharged from the oil drain path 20 .

Further, as described above, the sealing device 17 according to the present invention does not use the oil pressure inside the pressurizing chamber 16 as it is to perform the sealing action, so it simultaneously shields and seals the pressurizing chamber 16a and seals the pressurized chamber 16a. It is also possible to shield and seal both circumferential ends of 16b.

Therefore, if both ends of the oil drain chamber 16b in the axial direction are shielded and sealed, for example, by a sealing device (not shown) having the same structure as the sealing device 18, the oil draining chamber 16b will also be sealed like the pressurizing chamber 16a. By making the lower surface 22c of the distal end of the seal body 22 an inclined surface like the upper surface 22b, the same effects as described above can be achieved.

For example, in the embodiment, the oil feed path 19 and the oil drain path 2
If the connection between 0 and the oil feeding mechanism and oil draining mechanism is switchable, the upper pressurizing chamber 16a
Alternatively, hydraulic pressure can be selectively applied to the lower pressurizing chamber 16b.

Furthermore, in the embodiment, if the oil drain path 20 is also connected to the oil supply mechanism (not shown), the upper pressurizing chamber 16a
It is also possible to apply pressure-increasing hydraulic pressure to the pressure chamber 16b and the lower pressurizing chamber 16b. If this is done, the roll 11 is moved to the seventh position.
It can be placed in the middle of a multi-stage roll device as shown in the figure.

For example, a high pressure is applied to the upper pressurizing chamber 16a to apply good pressure treatment to the strip 33 using the roll 11 and the upper roll 32, and a relatively low pressure is applied to the lower pressurizing chamber 16b. , while preventing concave deflection of the roll 11,
The feeding action of the strip-like article 33 can be performed satisfactorily with the roll 34 below the roll 11.

Note that the configuration of the sealing device 17 according to the present invention is not limited to the above embodiment, and for example, the pressing means 35 for pressing the sealing body 22 may be a spring disposed within the groove 21. It may also be configured with

As is clear from the above description, the sealing device of the present invention includes a seal body that is slidably provided on the shaft in the radial direction.
Regardless of the pressure medium in the pressurizing chamber, the inner circumferential surface of the shell is pressed at a predetermined pressure through the pressing means, and the side surface of the tip of the seal body facing the pressurizing chamber is pressed against the inner circumferential surface of the shell by the pressure in the pressurizing chamber. Since the tip is formed on an inclined surface that generates a component force that tries to bite into the inner circumferential surface of the shell and a component force that tries to separate it from the inner circumferential surface of the shell, the pressure in the pressurized chamber is reduced. It is possible to effectively prevent the inconvenience of the sealing force becoming insufficient or becoming larger than necessary due to changes, thus preventing the occurrence of various troubles as mentioned at the beginning, and ensuring good sealing over a long period of time. It is something that can perform its functions.

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 any strip shape. The pressure treatment of the product can be performed satisfactorily while fully demonstrating the function of the roll.

Moreover, since the sealing force of the seal body does not become larger than necessary, while maintaining a good sealing effect,
It is also possible to speed up the pressure treatment by rotating the shell at high speed.

Furthermore, according to the conventional sealing device as mentioned at the beginning,
When the intermediate chamber formed between the inner circumferential surface of the shell and the outer circumferential surface of the shaft is partitioned into two chambers in the circumferential direction by a sealing device, both of the partitioned chambers are configured as a pressurizing chamber. However, according to the sealing device of the present invention, it is possible to configure each of the compartments as a pressurizing chamber, and it is possible to correspond to the properties of the product to be pressure treated. Its practical value is extremely high.

[Brief explanation of the drawing]

Fig. 1 is a longitudinal sectional front view showing a conventional sealing device (showing the same parts as Fig. 4), and Figs. 2 to 10 show an embodiment of a roll equipped with a sealing device according to the present invention. Fig. 2 is a longitudinal front view (the cross section is along the line ■-■ in Fig. 3), Fig. 3 is a longitudinal side view (the cross section is along the line m-m in Fig. 2), and Fig. 4 The figure 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 explanatory diagram of the action of the seal body.
Fig. 7 is a diagram of the use state of the roll, Fig. 8 is a schematic vertical sectional side view showing a state in which hydraulic pressure is applied to the pressurizing chamber, Fig. 9 is a sectional view taken along the line IX-IX in Fig. 8, and Fig. 10 is FIG. 8 is a sectional view taken along the line X-X in FIG. 8; 11...Roll, 12...Shell, 1
2a... Inner peripheral surface of shell, 13... Shirt t., 16a... Pressure chamber, 16b...
・・Drainage chamber (pressurized chamber), 17・・・・Seal equipment L2
2... Seal body, 22b... Upper surface of the tip of the seal body, 22c... Lower surface of the tip of the seal body, 35... Pressing means.

Claims (1)

[Scope of utility model registration request] A cylindrical shell is rotatably supported by a shaft inserted concentrically through the cylindrical shell, and a pressurizing chamber extending in the axial direction into which a pressure medium is press-fitted between the opposing peripheral surfaces of the two is defined. In a certain roll, a sealing device for shielding and sealing both circumferential ends of the pressurizing chamber along the axial direction, the pressurizing chamber being arranged on the shaft side so that the cross-sectional shape of the tip part is tapered. A seal body extending in the axial direction and having an inclined side surface at the tip facing the shell is supported so as to be slidable in the radial direction of the shell, and the tip of the seal body is pressed against the inner circumferential surface of the shell by a predetermined pressure. A sealing device for a roll, characterized in that it is provided with a pressing means for pressing the roll.