JPH0665889A - Variable crown roll for high rolling reduction - Google Patents

Abstract

PURPOSE:To press a web with pressing force uniform in lateral direction by supporting a shaft in non-rotating state with both ends of a shell using bearings and placing a number of pressing pistons in axial direction in a pressure chamber formed between the body part of the shell and the shaft. CONSTITUTION:A shaft 3 is supported in non-rotating state with the shafts 6, 6 of a shell 2 using bearings 10, 10. A divided pressure chamber 15 is formed between the body part 5 of the shell and the shaft and a number of pressing pistons 26 are arranged along the axial direction. An oil is supplied with pressure into the pressure chamber and to each pressing piston to effect the outward deformation of the part of the body contacting with the counter roll.

Description

Detailed Description of the Invention

[0001]

The present invention relates to rubber, asbestos,
The present invention relates to a crown variable roll for high pressure application, which is intended for various non-metal or metal webs such as paper, synthetic resin, iron, aluminum foil, and copper foil.

[0002]

2. Description of the Related Art When a web is compressed between rolls and subjected to a pressure treatment, the rolls are not a completely rigid body, so that the rolls inevitably undergo a curved deformation as shown in FIG. Both end sides are higher than the center side, and non-uniform pressure acts on the web W. Therefore, for the purpose of correcting the curving deformation of the roll, a crown roll in which the central portion of the roll is made inwardly convex is used. However, the pressure to be applied to the web varies depending on the hardness, thickness and material of the web, so it is necessary to prepare a large number of rolls with different crown amounts corresponding to these, which is The above is impossible. For this reason, it was not possible to cope with the composite changes in hardness and thickness of all webs.

From these points of view, there has already been proposed a calender roll whose crown amount can be arbitrarily adjusted by utilizing hydraulic pressure. It is a pressurizing chamber type calender roll shown in FIG. 10, which fixes both ends of the shaft 31 to the machine body in a non-rotating state via self-aligning bushes 32. The shell 33 is fitted onto the shaft 31. The left and right ends of the shell 33 are rotatably supported on the shaft 31 via bearings 35, 35 formed by self-aligning roller bearings, and the shell 33 is rotationally driven by external power. The gap between the shaft 31 and the shell 33 is divided into two upper and lower pressure chambers 39 and drain chambers 40 by the left and right end face seals 36, 36 and the front and rear axial seals 37, 37. Then, the oil is pressure-fed to the pressurizing chamber 39 through the passage 41 provided in the shaft 31, a part of this oil flows into the drain chamber 40 through the seals 36 and 37, and then through another passage 42 provided in the shaft 31. It is to be returned to the hydraulic unit. Such a form is found, for example, in Japanese Patent Publication No. 58-46599.

Incidentally, the axial seal 37 there is shown in FIG.
In the following description, the sealing material 13a has a wedge-shaped cross section,
The leaf spring 13b and the leaf spring 13b that press this so as to swing
Is provided on the shaft 31. The spacer 13c is provided for fixing to the shaft 31, and the tip of the sealing material 13a is in contact with the inner peripheral surface of the shell 33 via an oil film. The axial seals 37, 37 have a function of increasing the contact pressure of the sealing material 13a with the shell 33 as the hydraulic pressure of the pressurizing chamber 39 increases.
In addition, this calender roll is designed so that the shell 33 is hydraulically curved to obtain a crown, so that the shell 3
Compared with the type that inflates 3 with hydraulic pressure, it has the characteristic that it requires lower hydraulic pressure.

[0005]

However, in the improved calendar roll 1 described above, both ends of the shaft 31 are supported by the body. Therefore, when both ends of the shaft 31 are flexibly deformed by receiving a load as shown in FIG. 11 during the rolling of the web, the axial center of the shell 33 supported by the bearings 35 of the shaft 31 is "displaced" in the downward direction. Become.
The "positional shift" phenomenon of the axial center of the shell 33 affects the finished plate thickness of the web, and a web having a desired plate thickness cannot be obtained. Therefore, this is a new factor in that the shaft support position must be readjusted separately from the hydraulic pressure according to the hardness and thickness of the web, and this adjustment work was extremely difficult.

Further, this pressure chamber type calendar roll is
As the hydraulic pressure introduced into the pressurizing chamber 39 increases, the shell 3
Since the contact pressure of the sealing material 13a with respect to No. 3 increases and the amount of wear and the amount of heat generation increase, the hydraulic pressure applied to the pressurizing chamber 39 is limited. Therefore, it is possible to cope with the case of a web such as paper which can be calendered with a relatively low hydraulic pressure (nip linear pressure applied to the contact portion of the shell 33 is about 500 to 600 kg / cm), but a web such as an aluminum plate or a steel plate is skin-passed. (The nip line pressure is about 2000 to 300
In case of 0kg / cm), we cannot handle it.

Therefore, an object of the present invention is to further develop and improve the pressurizing treatment of the web with a uniform pressure in the width direction while following the above-mentioned conventional type so as to prevent the displacement phenomenon of the shell. The purpose of the present invention is to obtain a crown variable roll in which the factor of the plate thickness variation is eliminated, and thus the crown amount of the shell of the shell can be easily adjusted only by considering the conditions on the web side. Another object of the present invention is to provide a crown variable roll for high pressure, which can be applied not only to a non-metallic web such as paper or resin but also to a skin pass of a metallic web such as aluminum or iron.

[0008]

A crown variable roll according to the present invention comprises a cylindrical shell 2 which is rotatably supported as shown in FIG. 1, and a shaft 3 which is inserted into the shell 2 in a non-rotating state. That is, the shell 2 has hollow shaft portions 6 and 6 at both ends of the hollow cylindrical body portion 5, and the shaft portions 6 and 6 are rotatably mounted on the airframe side via bearings 7 and 7. Being supported, both ends of the shaft 3 are respectively supported inside the shaft portions 6 and 6 via bearings 10 and, and between the body portion 5 of the shell 2 and the shaft 3, Body 5
The pressurizing chamber 15 is provided inside the part of the pressurizing chamber 15 that faces the mating roll 21, and the pressurizing chambers 15 are provided with the pressurizing pistons 26 facing the many mating rolls 21 in the axial direction. It is required that the pressurized oil be introduced from the outside to the respective pressurizing pistons 26 via the respective passages 22 and 30 in the shaft 3. It should be noted that the hydraulic pressure introduced to the pressurizing chamber 15 and the pressurizing piston 26 causes the web W to pass through the body portion 5.
There is still a limit to the pressure that can be applied to. Therefore, when it is desired to apply a pressure exceeding this to the web W, it is also effective to form a crown corresponding to the necessary nip linear pressure on the outer peripheral surface of the body portion 5 in advance in a convex shape.

[0009]

The body 5 of the shell 2 is pressed against the opposite roll 21 by sandwiching the web W, and the central portion of the entire crown variable roll 1 tends to be curved and deformed in the direction of arrow P in FIG. At this time, in the lower calender roll 1, the body part 5 of the shell 2 has a part side (upper half part side) that comes into pressure contact with the mating roll 21 due to the hydraulic pressure introduced to the pressurizing chamber 15 and a number of pressurizing pistons 26. Since the shaft 3 is pressed, the shaft 3 is curved in the direction of the arrow P, but the nip line of the body portion 5 becomes a straight line. Depending on the opponent roll 21, etc., both rolls 1 and 2
The nip line 1 has a straight line or a curved shape. In any case, the web W has 1 roll on both sides across the width.
A uniform pressurizing action is received between 21 and 21. Since both shaft portions 6 and 6 of the shell 2 are directly rotatably supported with respect to the machine body and the shaft 3 is supported inside the shaft portions 6 and 6, the support shaft center of the shell 2 itself with respect to the machine body There is no displacement in the position. The portion of the body portion 5 that is in pressure contact with the mating roll 21 is pressed outward by the hydraulic pressure acting from the pressurizing chamber 15 side and the hydraulic pressure acting from the multiple pressurizing pistons 26 side, so it should be added to the web W. The pressure can be dramatically increased.

[0010]

As described above, in the variable crown roll 1 of the present invention, since the support shaft center of the shell 2 itself with respect to the machine body is not displaced, a web having a desired plate thickness can be obtained and the shell 2 can be obtained. Regarding the generation of the crown in the body portion 5, it is sufficient to adjust the hydraulic pressure introduced to the pressurizing chamber 15 and each pressurizing piston 26 in consideration of only the conditions on the web side, and it is possible to change the hardness and thickness of the web. Can respond promptly. As a result, the web can be pressed uniformly in the width direction.
The portion of the body portion 5 that is in pressure contact with the opposing roll 21 is a pressurizing chamber 15
And the large number of pressurizing pistons 26 are used to press outward, so that the pressure applied to the web W can be dramatically increased while the conventional seal structure is used as it is. It can be effectively applied to the skin pass of.

[0011]

1 to 8 show an embodiment of a crown variable roll 1 according to the present invention, which comprises a shell 2 which is rotatably supported and a coaxially inserted non-rotating state inside the shell 2. And a shaft 3 to be driven. As shown in FIG. 1, the shell 2 is composed of a hollow cylindrical large-diameter body portion 5 and hollow small-diameter shaft portions 6 and 6 connected to the left and right ends thereof.
In the figure, in order to improve the workability of assembling, one end side of the shaft portions 6, 6 is fitted into the open end of the body portion 5 and fixed by screws. The body portion 5 has a length of 1500 mm, an outer peripheral diameter of 650 mm, and an inner peripheral diameter of 460 mm, and a middle convex crown is formed in advance on the outer peripheral surface. This crown has a nip linear pressure of about 2000 kg in the portion of the body 5 facing the opposing roll 21.
It corresponds to / cm. In other words, when the pressing force is applied to both ends of the shell 2 until the nip line pressure reaches the above value, the nip line becomes a straight taper crown.

The shell 2 has both shaft portions 6 and 6 supported on the arm of the machine body through bearings 7 and 7 which are self-aligning roller bearings. Then, in the figure, when rotational power is externally input to the power input end 9 provided on the right shaft portion 6, the shell 2 rotates. The shaft 3 has a large central portion 3a and both end portions 3a.
b and 3b are formed to have a small diameter, and both end portions 3b and 3b having a small diameter are arranged so that the central portion 3a having a large diameter faces the body portion 5 of the shell 2.
Is a shaft portion 6 of the shell 2 via a bearing 10 or 10 by a self-aligning roller bearing or a bushing capable of self-aligning.
・ It is supported inside 6. The shafts 3 and the shell 2 have their axes aligned with each other. Each bearing 10 is a shell 2
Is disposed at substantially the same position in the axial direction as the bearing 7 that supports the vehicle body side. In the drawing, the left end of the shaft 3 projects outward from the left shaft portion 6, and a positioning ring 11 is fixed to this protruding portion, and the positioning ring 11 is connected to the machine body side to prevent the shaft 3 from rotating. There is.

Body portion 5 of shell 2 and central portion 3 of shaft 3
A gap is formed around the entire circumference with a, and the gap is divided into an upper pressure chamber 15 and a drain chamber 16 by the left and right end face seals 12 and the front and rear axial seals 13 and 13. I am doing it. That is, as the end face seal 12, as shown in FIGS. 1 and 2, movable rings 17 are attached to both left and right inner sides of the body 5, and fixed rings 19 are provided on the outer periphery of the shaft 3 so as to face the movable rings 17. . Fixed ring 19
2 has a sealing material 20 planted therein, as shown in FIG.
Its tip is elastically brought into contact with the sealing surface of the movable ring 17.

The axial seal 13 is provided on the outer peripheral surface of the shaft 3 in the axial direction with a phase difference of 180 ° in the circumferential direction. As shown in FIG. 3, the tip of the axial seal 13 forms an oil film on the inner peripheral surface of the shell 2. Seal member 13a having a wedge-shaped cross section, and a leaf spring 13b that presses it in a swingable manner, and a leaf spring 13b.
And a spacer 13c for fixing to the central portion 3a of the shaft 3. The axial seal 13 has a function of increasing the contact pressure of the sealing material 13a as the hydraulic pressure in the pressurizing chamber 15 increases, and prevents excessive oil leakage from the pressurizing chamber 15. The axial seal 13 divides the gap between the body 5 and the shaft 3 into upper and lower parts. The upper half of the gap between the shell 2 and the shaft 3 is the pressurizing chamber 15, and the lower half is the drain chamber 16. It is set.

The pressurizing chamber 15 is located on the side that is in pressure contact with the opposing roll 21 across the web W, and when hydraulic pressure is introduced from the outside through the oil introduction passage 22 provided in the shaft 3. , The crown is generated by pressing the barrel 5 outward from the inside of the barrel 5. Part of the oil introduced into the pressurizing chamber 15 is partially drained through the seals 12 and 13 to the drain chamber 16
Flow into. Separately, the shaft 3 is provided with a passage 23 through which oil flows into and out of the drain chamber 16. These passages 22
23 is connected to the hydraulic unit 25 by utilizing that the left end of the shaft 3 projects from the shell 2.

Further, in the pressurizing chamber 15, a large number of pressurizing pistons 26 for pressing the body 5 outward from the inside to generate a crown are arranged at equal intervals in the axial direction. As shown in FIGS. 4 to 6, each pressurizing piston 26 is radially slidably held by a cylinder 27 formed in the central portion 3a of the shaft 3, and pressure pockets 26a are provided at four corners on the top surface thereof. Concave pressure area 26 in the center
b are formed respectively. In the pressure pocket 26a,
Passage 29 in shaft 3 and passage 2 in pressurizing piston 26
A constant hydraulic pressure acts from 6c through the throttle, whereby a constant gap is formed between the top surface of the pressurizing piston 26 and the inner peripheral surface of the shell 2. The passage 29 in the shaft 3 leading to the pressure pocket 26a is omitted in FIG.

The pressure area 26b is connected to the cylinder 27 through a pressure hole 26d in the pressure piston 26.
The oil leading to the cylinder 27 from the oil introduction passage 30 provided in the shaft 3
It acts on the inner surface of the body 5 via the pressure area 26b. At that time, some oil flows out from the gap between the top surface of the pressurizing piston 26 and the inner peripheral surface of the body portion 5 to lubricate them. The pressure piston 26 receives pressure from the top surface side in a state where the hydraulic pressure is introduced into the pressure area 26b, but the pressure piston 26 is pressed against the body portion 5 side due to the difference in pressure receiving area between the top surface and the piston lower surface. Energized. Therefore, even if the body portion 5 bends and deforms downward or upward, the body portion 5 and the pressure piston 2
A constant gap is always maintained between the top surface of 6 and the pressure pocket 26a, and in this state, the pressure piston 26 slides in the cylinder 27 in the radial direction.

The hydraulic unit 25 guides the oil sucked up from the tank by the pump through the heat exchanger and the filter to the pressure regulator, distributes the oil by the pressure regulator and introduces it into the passages 22, 23, 29 and 30. To do. Oil is introduced at a predetermined high pressure into the passage 22 to the pressurizing chamber 15, the passage 29 to the pressure pocket 26a, and the passage 30 to the cylinder 27. An operation panel is connected to the pressure regulator, and when a signal is input from the outside to the pressure regulator via the operation panel, each passage 22, 23, ...
The hydraulic pressure introduced to 29 and 30 is adjusted.

When the above-mentioned crown variable roll 1 is used, as shown in FIG. 7, the mating roll 21 is arranged above the crown variable roll 1 with the web W interposed therebetween. Now, the opponent roll 21 has the same specifications as the crown variable roll 1. As shown in FIG. 8, the nip line pressure of the body parts 5, 5 is about 2
If pressure is applied to the shaft parts 6 and 6 at both ends in the direction in which both rolls 1 and 21 come close to each other until reaching 000 kg / cm,
21 is curved and deformed in the vertical direction as a whole, and the body portion 5
The crown of is corrected and the nip line becomes a straight line. If a pressing force is further applied to the shaft portions 6 at both ends from this state, a concave concave curved deformation occurs on the nip line side of the body portions 5 and 5 and the thickness of the web W tends to be non-uniform in the width direction. However, since the oil is pumped to the pressurizing chamber 15 and the plurality of pressurizing pistons 26, the shaft 3 is curved and deformed, but
No curving deformation occurs in the nip line of the body portions 5 and 5, and the nip line is maintained in a straight line. As a result, the web W is uniformly pressed in the width direction.

Next, the numerical value of the function of this roll is given.
One example will be described. Pressure chamber 1 without pressure piston 26
In the case of only 5, considering the wear limit of the seals 12 and 13, it is possible to apply a pressure of up to 180 tons to the shaft portions 6 of the shell 2 and a hydraulic pressure of up to 30 kg / cm ² to the pressurizing chamber 15. On the other hand, in the case of only the pressurizing piston 26, in consideration of the limit amount of oil leaking from the gap between the shell 2 and the pressurizing piston 26, a pressure of up to 200 tons is applied to the shaft portions 6 and 6 of the shell 2 to pressurize the pressurizing chamber. Hydraulic pressure can be applied to 15 up to 120 kg / cm ² . However, the crown variable roll 1 of the present invention has both functions. Therefore, the pressurizing chamber 1
Although the upper limit of the hydraulic pressure applied to 5 and the pressurizing piston 26 is almost the same as the conventional one, it is possible to apply a maximum pressure of about 180 + 200 tons to the shaft portions 6 and 6 at both ends with the nip line kept straight. It can be effectively applied to the skin pass of the web W made of. Since the crown corresponding to the minimum nip linear pressure of 2000 kg / cm is provided on the outer peripheral surface of the body portion 5, the pressing force obtained by the pressurizing chamber 15 and the pressurizing piston 26 should be applied to the web W from the linear pressure. This is particularly effective when the web W is processed under high pressure such as skin pass.

Since the shaft portions 6 and 6 of the shell 2 are directly supported on the machine body side through the bearings 7 and the shaft 3 is supported inside the shaft portions 6 and 6, the shell 2 of the shell 2 with respect to the machine body is supported. The support point does not move up and down due to the applied pressure, and for example, the lower shell 2 and especially the body portion 5 thereof do not shift downward.
Therefore, it is not necessary to consider the positional deviation of the axial center of the shell 2, and it suffices to control the hydraulic pressure so as to correspond to the pressing force according to the hardness, thickness and material of the web W and to determine the crown amount. . The bearing 10 that supports the shaft 3
If is arranged at substantially the same position as the bearing 7 in the axial direction,
Since the load applied to the shaft 3 is directly supported by the bearing 7, there is no displacement of the axial center of the shell 2.

The shell 2 shown in the figure has a body part 5 and a separate shaft part 6.6.
Since it is designed to be connected, the inner diameter of the body portion 5 can be set large, and the pressurizing chamber 15 can also be formed large in diameter in the axial direction thereof. Therefore, the crown amount of the body portion 5 can be freely adjusted at low pressure. Therefore, a simple hydraulic mechanism including a pump and the like is sufficient. In addition, if the areas of the pressurizing chamber 15 and the drain chamber 16 are made large, there is an advantage that heat can be efficiently exchanged in each room even when the crown variable roll 1 is used while being heated or cooled.

(Another embodiment) The crown to be provided in advance on the body portion 5 may be appropriately changed depending on the pressure applied to the web. However, the crown may not be provided on the body portion 5 and the crown may be formed only by the hydraulic pressure introduced to the pressurizing chamber 15 and the plurality of pressurizing pistons 26. It goes without saying that the counterpart roll 21 is not limited to the calendar roll 1 of the present invention, and may be a normal roll.

[Brief description of drawings]

FIG. 1 is an overall vertical sectional front view.

FIG. 2 is a partially cutaway perspective view of a main part.

FIG. 3 is a cross-sectional view of an axial seal portion.

4 is a cross-sectional view taken along the line AA in FIG.

FIG. 5 is a plan view of a piston.

6 is a sectional view taken along line BB in FIG.

FIG. 7 is a perspective view showing a usage state of a crown variable roll.

FIG. 8 is a schematic vertical sectional front view for explaining the operation of the crown variable roll.

FIG. 9 is a front view of a conventional roll.

FIG. 10 is a vertical sectional front view of an improved conventional calendar roll.

11 is a schematic vertical sectional front view for explaining the operation of the calendar roll of FIG.

[Explanation of symbols]

 1 Crown Variable Roll 2 Shell 3 Shaft 5 Body 6 Shaft 7 Bearing 10 Bearing 12 End Face Seal 13 Axial Seal 15 Pressurizing Chamber 16 Drain Chamber 21 Opposite Roll 22 Passage 26 Pressurizing Piston 30 Passage W Web

Claims (1)

[Claims] 1. A cylindrical shell 2 that is rotatably supported, and a shaft 3 that is inserted into the shell 2 in a non-rotating state. The shell 2 is hollow at both ends of a hollow cylindrical body 5. Shaft 6
.6, and each shaft portion 6/6 is rotatably supported on the airframe side via bearings 7/7. The shaft 3 has shaft portions 6 at both ends via bearings 10/10.
6 are respectively supported on the inside of the shell 2. Between the body 5 of the shell 2 and the shaft 3, a pressure chamber 15 is provided inside the portion of the body 5 facing the counterpart roll 21. 15, a pressure piston 26 is arranged on the shaft 3 side along the axial direction to face a large number of mating rolls 21. In the pressure chamber 15 and each pressure piston 26, pressure oil is stored in the shaft 3. A variable crown crown roll for high pressure, characterized in that it is guided from the outside through the passages 22 and 30.