JPH05323555A - Roll type pressure device and method of compensating deflection of pressure roll - Google Patents

Abstract

PURPOSE: To provide a large load roll type pressuring device including a deflection compensating means having simple constitution and a new method for compensating the deflection of a pressure roll. CONSTITUTION: A nip 15 is formed by a 1st solid roll 10 and a 2nd roll 20 for compensating deflection. The 2nd roll 20 has an outer cylinder 22 and a supporting shaft 30 for holding the outer cylinder 22. A pair of load transmission bearings 35, 36 are arranged between the cylinder 22 and the shaft 30. Bearings having action capable of interrupting the transmission of bending moment between the cylinder 22 and the shaft 30 are used for the bearings 35, 36. These bearings 35, 36 are respectively arranged on positions separated from the axial direction center of the 2nd roll 20 respectively by an equal distance on both the sides of the center. The distance is set up so as to match the deflected curves of both the rolls 10, 20 when uniform pressure is applied between the 1st and 2nd rolls 10, 20.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a roll type pressure device, and more particularly to a high pressure type pressure device used for pressure development of a latent image and a method for compensating for deflection of a pressure roll.

[0002]

2. Description of the Prior Art For example, Singh US Pat.
90,391 (issued November 9, 1976) and Haugen, U.S. Pat. No. 4,356,764 (1
As disclosed in No. 2, 982), a roll type pressure device, that is, a nip (gap) for applying pressure to a non-pressurized object is formed between a plurality of pressure rolls. Pressure devices are conventionally used to fix toner images to sheet or web materials. The fixing of a fusible toner image usually requires the use of a roll-type pressure device that is capable of uniformly applying a pressure on the order of 1000 pounds per square inch to the entire image. However, pressurizers designed to provide uniform pressure tend to not operate properly when used to apply high pressure.

Examples of non-pressurized materials requiring substantially high pressure include US Pat. Nos. 4,440,846 and 4,4
No. 339,209 (Transferee: Mead Corporation)
And the photosensitive microcapsule medium disclosed in US Pat. In these microcapsule media, a layer of photosensitive microcapsules containing a photosensitive composition is provided on a sheet material. According to the description in the above patent, a layer of microcapsules is exposed to radiation having actinic radiation according to image information, and then pressure is applied to rupture the microcapsules to form a latent image, and the latent image is developed. By doing so, a visible image is formed. In the case of a single sheet type medium, the image forming substance (for example, a colorless color developing agent) is provided on the same sheet as the developer. On the other hand, in the case of the double sheet type medium, the image forming substance is provided on a sheet different from the developing sheet on which the developer is provided. In either case, one or two sheets are passed through the nip of a roll-type pressure device to apply pressure to the sheet-shaped medium to develop an image. To develop such an image forming microcapsule medium under pressure, 6000 to 1 square inch
A pressure of 8000 pounds is typically applied.

[0004]

Attempts have been made in the past to produce very hard pressure rolls. A hard roll is a pressure roll that has very little deflection or bending when a large load is applied. An example of such a pressure roll is U.S. Pat. No. 3,618,1 issued to Vernazza et al. On Nov. 9, 1971.
The pressure roll disclosed in No. 90 is mentioned. The pressure roll of this patent exhibits a relatively high hardness, and the bending of the outer cylinder forming the outer layer of the pressure roll is not affected by the bending of the support shaft due to the action of the pair of self-aligning bearings. However, this patent does not disclose any means for compensating for the bending of the pressure roll itself. That is, any slight bending or bending is significant under the high pressure conditions required to rupture the microcapsules as described above (ie, obstacles to applying uniform pressure). It is necessary to compensate for this bending effect by some means.

When the roll-type pressure device as a pressure developing machine is loaded, some bending of the pressure roll is unavoidable. This bending is not always undesirable. However, in order to pass the sheet or web material through the nip of the pressure roll without undue damage, stretching, or wrinkling of the sheet or web material, and to provide uniform pressure along the nip, the pressure Means must be provided to compensate for roll deflection. As such a compensating means, it is conceivable to use a pressure roll having an inclined axis and / or a pressure roll having a crown in a three- to four-roll type pressure device, for example.
In addition, as a compensating means, a pressure roll having a very complicated structure and a special device for applying a load to the pressure roll have been made. Many of these compensation measures are very complex and produce unwanted side effects, or
It has been found that it is effective only when pressing a sheet having a limited width or applying a pressure in a limited range.

The present invention has been made in view of the above points, and an object of the present invention is to provide a roll-type pressurizing device having a deflection compensating means having a substantially simplified structure, and in particular to impart a relatively high pressure. To provide a roll-type pressure device suitable for

Another object of the present invention is to provide a new method of compensating for the deflection of a pressure roll when using a roll type pressure device.

[0008]

The present invention is particularly preferable when applied to a pressurizing device having two pressure rolls, but the scope of application of the present invention is not limited to this. It also includes application to other types of pressure devices using three to four rolls.

First, it goes without saying that a pressure roll is used which is capable of aligning or matching the deflection curves of both pressure rolls (that is, the contour lines appearing along the nip) in the nip between the pressure rolls with each other. Alignment of the deflection curves cannot generally be achieved by arranging pressure rolls of the same construction facing each other. This is because when the pressure rolls having the same structure are used, the bending moment of one pressure roll is positive and that of the other pressure roll is negative.
Uniform pressure distribution along the nip by using multiple pressure rolls of different constructions and shapes, or by controlling the loading points on the rolls so that the deflection curves match when the pressure rolls are loaded. The pressure is surely applied.

Further, in the roll type pressurizing device for applying high pressure, it is desirable that the surface of the plurality of pressure rolls forming the nip has a cylindrical shape. The columnar shape not only eliminates the need for complicated machining and surface grinding, but it also creates scratches and slips when high pressure is applied, for example, when a ground roll is used in pairs with a cylindrical roll. Multiple pressure rolls can work well together without causing the like. The remarkable effect of the present invention is that the deflection of the pressure roll can be compensated while the nip forming surface of the pressure roll is kept cylindrical.

The pressure roll of the pressure device of the present invention comprises a sleeve-shaped outer cylinder attached to the support shaft. In this outer cylinder, the bending moment of the support shaft does not affect the bending moment of the outer cylinder. In a preferred embodiment of the present invention, a load is applied to the outer cylinder from the support shaft via a self-aligning bearing. The two self-aligning bearings as described above are provided at positions equidistant from the axial center of the outer cylinder so that the outer cylinder bends without being affected by the bending moment of the support shaft.

The pressurizing device of one embodiment of the present invention has two flexible pressure rolls that are opposed to each other to form a nip. At least one of the flexible pressure rolls has a cylindrical outer cylinder and a support shaft provided inside the outer cylinder and concentric with the outer cylinder. The support shaft and the outer cylinder are connected only via load transmitting means (for example, a self-aligning bearing) that transmits a load other than a torque load (bending moment). When a load is applied to the support shaft, this connection structure makes the deflection of the outer cylinder independent of the deflection of the support shaft. Therefore, the outer cylinder bends without being affected by the bending of the support shaft.

When carrying out the method of the present invention, the deflection curve of the pressure roll at the desired load is calculated by the general double integral of the equation of bending moment, or equivalent means. The deflection curve is calculated separately for each roll. Final deflection curve matching or matching is done by systematically varying parameters while comparing the deflection curves of both pressure rolls using a computer. These parameters are the bending stiffness of the pressure roll (value determined by the inner diameter, outer diameter and Young's modulus) and the spacing between the bearings on the support shaft.
In the case where both pressure rolls both have the outer cylinder and the support shaft, the parameters of both pressure rolls are changed.

A plurality of basic deflection curves for conforming the deflection curves along the entire effective length of the roll are obtained as described above. The above calculation and the subsequent deflection curve matching operation are substantially simplified by the fact that the outer cylinder can be treated as a cylindrical beam independent of its support axis.

The structure of the roll type pressure device of the present invention is particularly a pressure device comprising two pressure rolls, and both pressure rolls have an outer cylinder and a support shaft. Shows a remarkable effect. In the case of a device with such a configuration,
In matching the deflection curves of the pressure roll, more various adjustments can be made regarding the diameter and effective length of the pressure roll. That is, the flexibility for matching the shapes of the bending curves is easy. However, in the case of the two-roll type pressure device, only one roll has the roll structure of the present invention (structure having an outer cylinder and a support shaft), and the other roll may be a mere general roll. .. The solid roll is preferably cylindrical, but a roll having a crown or a roll having parallel or inclined axes may be appropriately used. Incidentally, one or more pressure rolls (backup rolls) having the roll structure of the present invention may be added to the pressurizing device in order to apply a load to the cylindrical pinch roll (pressure roll for nip formation). .. In any case, the flexure curve of the outer cylinder provided on the support shaft via the self-aligning bearing, whatever the pressure roll paired with it,
It is possible to match the deflection curve of the pair of pressure rolls.

[0016]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS FIG. 1 shows a two-roll type pressure device according to one embodiment of the present invention. This pressurizing device comprises a first roll 1
0, that is, having a solid cylindrical pressure roll. The first roll 10 has shafts 12, 12 at both ends thereof, and these shafts 12, 12 are supported by bearings 14, 14. Only the shaft portions 12, 12 of the first roll 10 are connected to the apparatus main body (not shown) for the purpose of driving this. The first roll is a general roll that has been conventionally seen, and the outer surface 16 has a cylindrical shape. Also,
The axial length of the first roll 10 is preferably set somewhat longer than the width of the sheet or web material processed by this roll.

The second roll 20 shown in FIG. 1 is a deflection compensating roll formed according to the technical idea of the present invention.
The second roll 20 has an outer cylinder 22 in the shape of a cylindrical sleeve. The outer cylinder 22 has an axial length equal to the axial length of the outer surface 16 of the first roll 10, and is a cylindrical outer surface that cooperates with the outer surface 16 of the first roll to form the nip 15. 24 is preferred. The outer cylinder 22 also has a cylindrical inner surface 25.

A support shaft 30 serves as a means for supporting the outer cylinder 22.
Is provided. The support shaft 30 is arranged coaxially with the outer cylinder 22 in a state where no load is applied. Support shaft 3
Both ends of 0 are supported by appropriate means, but the support shaft itself does not rotate.

As load receiving means for connecting the support shaft 30 and the outer cylinder 22, a pair of load transmitting bearings (self-aligning bearing or spherical bearing) 35 and 36 having the same structure are provided. A feature of these bearings 35 and 36 is that transmission of torque load (bending moment) between the outer cylinder 22 and the support shaft 30 is blocked. These self-aligning bearings 35, 3
Each of the 6 preferably has an inner race 37 attached to the outer surface of the support shaft 30 and an outer race 38 attached to the inner surface 25 of the outer cylinder 22.

The self-aligning bearings 35 and 36 are the support shafts 3.
At a distance of f from the geometric center line of the second roll 20 (a center line that passes through the center point in the axial direction and is orthogonal to the axis) at an axial distance from each other on 0. Each is provided (see FIG. 3). These self-aligning bearings 35, 3
6 is positioned at each position by, for example, the retaining rings 41, 41 fitted in the annular groove on the inner surface of the outer cylinder 22 and the spacer sleeve 42 attached to the support shaft 30.

Applying a pressure load in the above-mentioned pressurizing device is as follows.
As shown in FIG. 1, at the end of the support shaft 30, for example, an arrow 4
It is performed by applying a force in the direction indicated by 5. The reaction force at that time is generated by the bearings 14, 14 of the first roll 10. The direction of the reaction force is as indicated by arrow 46. Applying 600 lbs / linear inch of pressure per inch is not uncommon to produce pressures in the nip of the order of 6000 to 8000 pounds per square inch, as described above.

When the outer cylinder 22 is assumed to be a kind of beam, the outer cylinder 22 can be flexed by the action of the self-aligning bearings 35 and 36 without being affected by the bending (or bending) of the support shaft 30. In other words, since the bending moment of the support shaft 30 is not transmitted to the outer cylinder 22, the bending moment of the support shaft 30 can be ignored when calculating the deflection curve of the second roll 20. On the basis of this fact, the design of the second roll 20 and the calculation of its deflection curve (the contour line along the nip) is substantially simplified, and a deflection curve matching the deflection curve of the first roll 10 is This will allow the selection of appropriate design parameters for the second roll 20 to draw. Further, this configuration is efficient in increasing the bending stiffness of the outer cylinder 22.

Distance f between the self-aligning bearing and the center line 40
(See FIG. 3) and the parameters of the outer cylinder (for example, the wall thickness of the outer cylinder) so that the deflection of the outer cylinder 22 is appropriately controlled, and the roll nip between the first and second rolls is set. Appropriate values are chosen to produce uniform pressure along the axis. When the number of the second rolls 20 is one, the distances f and f between the bearing and the center line are equal to each other, and the center of the second rolls in the axial direction is the same regardless of the type of the second rolls. It is set based on the position. This distance f is selected according to the following logical series of steps. (1) It is assumed that a uniform load is applied along the nip between the first and second rolls. (2) Based on this assumption, the deflection curves of the first roll and the second roll are calculated. (3) While comparing the deflection curves of both rolls, the parameter change is repeated until the deflection curve of the outer cylinder 22 matches the shape of the deflection curve of the first roll.
If the shapes of the deflection curves match, the assumption regarding the uniform load between both rolls 10 and 20 is established, and
Both rolls flex in harmony to match their deflection curves. The above steps are valid regardless of the number of used second rolls having an outer tube which is not affected by bending of the support shaft.

More specifically, the first step in the roll design phase is that a uniformly distributed load, designated herein as "w", exists between the first and second rolls 10,20. Then assume that. By this assumption,
It is possible to design the model of each part shown in FIGS.

The next step is to calculate the roll deflection curve caused by the assumed distributed load w.
In the case of the first roll 10, its deflection curve is determined by double integrating the equation of bending moment. Since this equation is discontinuous at points B and C shown in FIG. 2, the solution of the double integral is separated into three parts, and each of them is evaluated separately. Then, the three solutions are combined into one by applying the common boundary conditions at points B and C.

The deflection curve of the outer cylinder 22 can be obtained by the same method. The deflection curve of the support shaft 30 is not calculated. Since the self-aligning bearings 35 and 36 prevent the transmission of the bending moment from the support shaft 30 to the outer cylinder 22, the deflection curve of the support shaft 30 is not important.

The bending shape of the first roll 10 when receiving a load as shown in FIG. 1 is a shape which is convexly convex downward. The actual shape of the bending curve and the degree of bending depend on the properties of the first roll 10, that is, mainly on the length L, the effective length l, the diameter D2, and the elastic modulus (Young's modulus) of the material (see FIG. 2).

The general shape of the deflection curve of the outer cylinder 22 when receiving a load as shown in FIG. 1 is also a shape which is convexly convex downward if the distance f between the bearings is sufficiently small. The actual shape of the deflection curve of the outer cylinder 22 and the degree of deflection are mainly the distance f, the effective length 1, the outer diameter OD,
It depends on the cylinder thickness (inner diameter ID) and the elastic modulus (Young's modulus) of the material (see FIG. 3).

The final step in the design phase is to make the deflection curve of the outer cylinder 22 and the deflection curve of the first roll 10 as close as possible to each other along the axial length of these pressure rolls, and the outer cylinder described above. Choosing different parameters for one roll. The first assumption holds that uniform loading is applied if the deflection curves match. This means that the first and second rolls exert a constant pressure on the unpressurized material over their entire effective length.

To match the deflection curves, a computer is programmed with equations that describe the deflection of the barrel and first roll. The relevant parameters are systematically varied within the DO loop network and then the group of deflection curves calculated for each roll is stored in memory. The closest deflection curve combination is found by comparing these stored deflection curves. In this case, the computer is instructed to output all combinations of deflection curves that match over the length of the roll with greater accuracy than the machining tolerances of the roll surface (within about 0.005 mm).

Table 1 below is a two-roll roll (nominal length 11 inches) manufactured based on the embodiment of FIG. 1 as an experimental example.
It is a table which shows the example of the value of the parameter of a mold pressurizing device.

[0032]

[Table 1] Below, margins

In Table 1, D1 is the diameter of the shaft portion 12, D2 is the diameter of the first roll body, a is the length of each shaft portion 12, and b is (L-1-2a) / 2. A value, e is a half of the difference between the actual length of the outer cylinder and the effective length l, and E is Young's modulus. Also, all units of values other than w and E are m
m.

The embodiment shown in FIGS. 1 to 4 has the simplest aspect of the invention, namely one solid first roll 10 and one hollow second roll 20. It is a pressure device. In this embodiment, the compensating roll, that is, the outer cylinder of the second roll 20, is not affected by the bending of the support shaft. However, the pressure device of the present invention may of course have a structure other than that shown in this embodiment. For example, two compensating rolls 20 may be used to form the nip. Such a construction is more flexible in matching the deflection curves and is therefore useful when it is desired to use larger loads and / or longer rolls. Further, one or more second rolls 20 may be used in the three roll press. In this case, a third roll having a small diameter may be interposed between the first roll 10 and the second roll 20, or the third roll may be provided between the two second rolls 20, 20. Rolls may be interposed. The latter configuration is desirable to increase the load bearing strength of the third roll.

Further, as described above, the first roll may have a cylindrical shape and may be provided on an axis parallel to the axis of the outer cylinder of the second roll, or in this field. As is well known, it may have an axis inclined with respect to the axis of the outer cylinder. Furthermore, the first roll may be provided with a crown for partial pressure compensation, as is known. However, the use of sloping axes or crowns can have the disadvantage of causing slip differences at different locations on the nip. In many cases, the tilting of the shaft or the use of a crown can be avoided by employing one or more secondary rolls and is not necessary. In other words, the present invention enables simplification of the structure of the pressure device when the length of the pressure roll and the magnitude of the load are limited. When it is considered necessary to employ a crown, the present invention may be employed in order to simplify the structure of the crown or as an addition to the crown. If the tilt of the axis is considered to be necessary, the present invention reduces the tilt angle and yet allows the flex curves to be accurately matched at a more limited tilt angle compared to the case without the present invention. May be adopted. Furthermore, the invention has the advantage that it makes it possible to use rolls of relatively long axial length without the use of pressure rolls with crowns or without tilting the axis of one of the pressure rolls.

FIGS. 5 and 6 show an example of a four-roll type pressure device using two second rolls 20.
The illustrated four-roll press is advantageous when applying pressure to a material having a relatively wide width, such as 24 inches or more. This pressurizing device includes an upper pressure roll 20a,
Lower pressure roll 20b and pair of intermediate pressure rolls 5
It is equipped with 0 and 51. The intermediate pressure rolls 50 and 51 are
Forming a nip 52 between them and being solid, its diameter is smaller than that of the upper and lower pressure rolls 20a, 20b. As can be seen from the side of the device shown in FIG.
The upper and lower pressure rolls 20a and 20b and the intermediate pressure rolls 50 and 51 have axes parallel to each other, and are arranged so as to be linearly stacked in a row and rotatable about each axis. Intermediate pressure roll 50,
51 acts as a roll for applying pressure to the non-pressurized material, and a nip 52 is formed between the two. That is, the sheet material or the web material is processed by passing the sheet material or the web material through the nip 52.

In this embodiment, the upper and lower pressure rolls 20
Each self-aligning bearing 3 with respect to the center line CL of a and 20b
5, 36 axial positions, ie distances a, b
Is set to a value suitable because the deflection curves of the upper and lower pressure rolls 20a and 20b coincide with each other.
In order to obtain a uniform pressure along the nip 52, the bending curves of the intermediate pressure rolls 50 and 51 should essentially match, but the bending stiffness of the intermediate pressure rolls 50 and 51 is the same as that of the upper and lower pressure rolls 20a and 20b. If it is sufficiently small in comparison (for example, about 5% or less), it can be ignored. It should be noted that if the deflection curves of the upper and lower pressure rolls 20a, 20b are matched, the bearing-centerline distances in the upper pressure roll 20a and the lower pressure roll 20b will be significantly different. If the length of the nip 52 is approximately 24 inches (63.45 cm), the support shaft 30
The load applied to each end of a is about 3000-3500 pounds. The hardness of the surface of the intermediate pressure rolls 50 and 51 is relatively high, and should be set to about 60 C in Rockwell hardness, for example. In order to increase the hardness of the surface, it is preferable to apply chrome plating. In order to avoid surface abrasion, the hardness of the surface of the outer cylinder 22 should be about 40 as Rockwell hardness.
It is better to set it to about 45C. A surface treatment of hard chrome plating may be applied to prevent surface corrosion and wear.

In designing the above apparatus, the above-mentioned three steps are carried out under the assumption that pressure is uniformly applied along the length direction of the nip 52 between the intermediate pressure rolls 50 and 51. That is, the upper and lower pressure rolls 20a, 2
The deflection curves of the outer cylinders 22a, 22b of 0b are calculated, and then the deflection curves of the outer cylinder 22a of the upper pressure roll 20a match the deflection curves 22b of the lower pressure roll 20b, the distance of the bearings 35, 36, the outer cylinder. Parameters such as the outer diameter and the inner diameter of 22a and 22b are sequentially changed. When these deflection curves match, the first assumption is the existence of a uniform pressure between the rolls 50, 51.

The four-roll type pressurizing device shown in FIGS. 5 and 6 can be designed by setting each parameter to the value shown in Table 2 below, for example. In Experimental Examples 5, 6, and 7 shown in Table 2, the length not including the shaft portion of each roll is 24 inches (610 mm), the intermediate pressure roll 50,
The diameter of 51 is 1.25 inches (31.8 mm). The outer cylinders 22a and 22b have a nominal diameter of about 3 inches, but the second moment of area of each of these outer cylinders is calculated based on the values of the outer diameter OD and the inner diameter ID shown in each experimental example of Table 2. It is a value calculated according to the formula of the second moment. Incidentally, in Table 2, the meanings of e, l, w and E, and the units of numerical values other than w and E are the same as in Table 1.

[0040]

[Table 2] Below, margins

As is apparent from Table 2, the combination of the distances a and b from the center line of the self-aligning bearing and the second moment of area of the outer cylinders 22a and 22b is determined by the two outer cylinders 22a and 22b.
The flexure curves are chosen to minimize the mismatch between them. That is, in the four-roll type pressure device of the above experimental example, the bending stiffness of the intermediate pressure rolls 50 and 51 can be ignored. In this way, a substantially constant pressure along the length of the nip is obtained in the working pressure device. For example, the mismatch value does not exceed the maximum mismatch value in the table, provided that it is within the normal range of load changes, such as occur during processing of web materials.

The preferred embodiment in which the bending of the support shaft is prevented from affecting the other parts of the pressure roll by using the self-aligning bearing has been described above, but instead of the self-aligning bearing, the supporting shaft is replaced. It goes without saying that any type of load transmission means for transmitting a load other than bending torque between the outer cylinder and the outer cylinder can be used. Although the support shaft arranged inside the outer cylinder has been described in the above-described embodiments, the present invention can also be implemented by providing the support shaft outside the outer cylinder as schematically shown in FIG. 7. It is possible. In the two-roll type pressure device of FIG. 7, the outer cylinders 100 and 102 for forming the nip are not supported from the inside. However, the outer cylinder 100 has the support roll 10 contacting its outer surface.
With the first load imparting shaft 104 having 5, 106, and the outer cylinder 102 has the second load imparting shaft 110 having the support rolls 111, 112 in contact with the outer surface thereof.
Are each supported from the outside. The support rolls 105, 106 on the shaft 104 and the support rolls 111, 112 on the shaft 110 are axially spaced from each other on both sides of the axial center of each shaft and equidistant from the center. To be done. However, as in the preceding embodiment, the distance between the support rolls 105 and 106 and the support roll 1
The intervals of 11, 112 are not equal. Outer cylinder 100, 102
Similar to the previous embodiment, the matching of the flexure curves is performed by appropriately selecting the distance between each pair of support rolls and / or the bending stiffness (inner diameter, outer diameter and Young's modulus) of the outer cylinders 100 and 102. Be seen. The apparatus of FIG. 7 has a disadvantage that the support roll is directly pressed against the outer surface of the outer cylinder, but has an advantage of simplifying the configuration of the apparatus itself. Further, in order to prevent the outer cylinder from being crushed (so that the outer cylinder keeps its cylindrical shape), a support disk 120 as shown may be provided at a position facing each of the support rolls in each outer cylinder.

In the case of a pressurizing device for applying pressure over a very wide width, the pressure roll 5 shown in FIGS.
It is advantageous to use one or both of 0 and 51 with a plurality of barrels having two different moments of inertia of area. In FIG. 8, a thick cylinder portion may be provided in the central portion 22d of the outer cylinder 22c, that is, a portion between the bearings 35 and 36. In addition, a step portion that extends in the circumferential direction may be provided on the inner surface of the outer cylinder 22c to provide a convenient means for fixing the bearing. The fact that the ratio of the central portion 22d to the end portion of the outer cylinder 22c can be selected is a convenient and useful parameter in matching the deflection curve of the outer cylinder with the deflection curve of the pressure roll contacting it.

Although the present invention has been described based on the specific embodiment, the present invention is not limited to the device having the configuration shown in the embodiment, and the scope of the invention described in the claims of the present application is not limited. It goes without saying that modifications or changes can be made to the embodiments without departing from the above.

[0045]

Since the present invention is constructed as described above, it has the following effects.

The apparatus and method of the present invention make it possible to apply a large load and obtain a uniform pressure along the nip.

According to the apparatus and method of the present invention, it is possible to obtain a desired pressure, for example, a uniform pressure along the nip by compensating the deflection of the pressure roll while maintaining the surface shape of the pressure roll in a cylindrical shape. it can. That is, the configuration and the execution of each step are simpler than those of the conventional apparatus and the deflection compensation method.

[Brief description of drawings]

FIG. 1 is a front view showing a cross section of a part of a two-roll type pressure device showing an embodiment of the present invention.

FIG. 2 is a front view of a solid roll which is one of the main parts of the pressure device shown in FIG.

FIG. 3 is a front view of an outer cylinder that is one of the main parts of the pressurizing device shown in FIG.

FIG. 4 is a front view of a support shaft that is one of the main parts of the pressurizing device shown in FIG.

FIG. 5 is a front view of a four-roll type pressure device showing another embodiment of the present invention.

6 is a side view of the pressure device of FIG.

FIG. 7 is a perspective view showing a modified example of the two-roll type pressure device shown in FIG.

FIG. 8 is an axial cross-sectional view showing a modified example of a pressure roll that can be used in the four-roll type pressure device of the type shown in FIGS. 5 and 6.

[Explanation of symbols]

 10 First Roll 20 Second Roll 22 Outer Cylinder 30 Support Shaft 35 Load Transfer Bearing (Self-Aligning Bearing) 36 Load Transfer Bearing (Self-Aligning Bearing) 50 Intermediate Pressure Roll 51 Intermediate Pressure Roll 52 Nip 20a Upper Pressure Roll 20b Lower pressure roll 22a Outer cylinder 22b Outer cylinder 30a Support shaft 30b Support shaft

Claims (2)

[Claims] 1. A pressure sensor comprising: two pressure rolls, which are arranged to face each other so as to form a nip therebetween; and a pair of load transmission bearings, and at least one of the two pressure rolls is an outer cylinder. And a support shaft provided separately from the outer cylinder inside the outer cylinder, wherein the pair of load transmission bearings is
The outer cylinder is interposed between the outer cylinder and the support shaft so that the outer cylinder can bend without being affected by the support shaft,
Furthermore, the pair of load transmission bearings are arranged one by one on both sides of the axial center of the outer cylinder and at positions equidistant from the center, and the distance is such that a pressure load under a certain condition is applied to the pressure roll. The roll-type pressurizing device is characterized in that the deflection curve of the outer cylinder in the nip is a distance set so as to match the deflection curve of the other pressure roll in the nip when applied to the nip. 2. A method for aligning the deflection curves of both pressure rolls in a nip between a pair of pressure rolls, comprising the steps of (a), (b), (c) and (d) below: Deflection compensation method. However, one of the pressure rolls includes an outer cylinder, and a support shaft provided inside the outer cylinder via a pair of load transmission bearings,
The load transmission bearings allow transmission of loads while blocking transmission of bending moment between the outer cylinder and the support shaft, and are arranged at intervals in the axial direction of the support shaft. The distance between the load transmission bearings is adjustable. (a) Step of selecting a specific pressure load applied to the pressure roll (b) Step of calculating a deflection curve of each pressure roll in the nip when the specific load is applied (c) Both calculated pressures Comparing roll deflection curves (d) adjusting the spacing between the load transfer bearings until the deflection curve of the outer cylinder matches the deflection curve of the other roll.