Roll structure with reduced deflection

Abstract

To reduce deflection along a center axis caused by a load acting in one direction perpendicular to the center axis in a roll structure which is rotatably supported at both ends on the center axis by bearings.SOLUTION: A roll structure has: a columnar trunk part 2; and end parts 3 extending outward in a center axis direction from end surfaces 2a at both sides of the trunk part and having a shaft diameter smaller than a shaft diameter of the trunk part. Each of the end parts is rotatably supported by a bearing device 4. The roll structure is configured to rotate around the center axis and concurrently feed a thin film or a thin plate along the rotation direction while pressing the thin film or the thin plate with a surface of the trunk part. The end surface of the trunk part is recessed at an outer periphery of the end part, and at least a part of the bearing device is fitted into a recess 2b.SELECTED DRAWING: Figure 1

Description

[Technical Field]

[0001] The present invention relates to a roll structure, such as a cylindrical press roll in a roll press device, which is rotatably supported by bearings on the central axis of a cylinder and in which a load acts in one direction perpendicular to the central axis. [Background technology]

[0002] A cylindrical press roll in a roll press device or the like rotates around a central axis and presses and delivers a thin film or sheet (hereinafter referred to as a "thin film, etc.") with its cylindrical surface along the direction of rotation. In such a roll structure, a reaction force from the thin film, etc., acts as a load in one direction perpendicular to the central axis. If the roll structure is significantly deflected along the central axis due to this load, it can interfere with the pressing and delivery of the thin film, etc. Therefore, various configurations have been proposed to reduce the deflection of such roll structures. For example, Patent Document 1 proposes a configuration in which bending mechanisms are provided at both ends of a press roll in a roll press device or the like to apply a bending load that curves the press roll in a direction opposite to the deflection caused by the load from the thin film, etc. [Prior art documents] [Patent documents]

[0003] [Patent Document 1] Patent No. 7176154 Summary of the Invention [Problem to be solved by the invention]

[0004] Generally, the deflection of a cylindrical body supported at both ends due to a load acting in the axial direction between supports is proportional to the fourth power of the distance between the supports. Therefore, in order to reduce the deflection of the cylindrical body due to a certain load, it is sufficient to reduce the distance between the supports. Therefore, in order to reduce the deflection of a roll structure such as a cylindrical press roll in a roll press device, it is sufficient to reduce the distance between the bearings at both ends of the roll structure. This knowledge is utilized in the present invention.

[0005] Thus, a primary object of the present invention is to reduce deflection along a central axis of a roll structure rotatably supported by bearings at both ends on the central axis in response to a load acting in one direction perpendicular to the central axis. [Means for solving the problem]

[0006] According to the present invention, the above-mentioned object is achieved by a roll structure having a cylindrical body portion and end portions extending outward in the direction of the central axis from each of the end faces on both sides thereof, the end portions having a smaller shaft diameter than the body portion, and each of the end portions being rotatably supported by a bearing device, the roll structure being configured to rotate around the central axis while pressing and feeding a thin film or thin plate with the surface of the body portion along the direction of rotation, and the end faces of the body portion are recessed in a concave shape on the outer periphery of the end portions, and at least a part of the bearing device is fitted into the concave recess.

[0007] In the above configuration, the "roll structure" may be a mechanism that rotates around a central axis, such as a cylindrical press roll in a roll press device, and delivers a thin film or sheet (hereinafter referred to as "thin film, etc.") along the direction of rotation while pressing it with the surface of its barrel. The "bearing" may be any type of bearing commonly used in this field.

[0008] According to the above configuration, since at least a portion of the bearing is recessed in the concave recess formed in the end face of the barrel portion, the distance between the bearing devices that rotatably support both end portions of the barrel portion can be shortened without changing the length of the barrel portion, compared to when no concave recess is formed in the end face, thereby reducing deflection of the barrel portion in the direction perpendicular to the central axis. Note that it is preferable that the recesses in the end face of the barrel portion are provided on both end faces, and that the bearing devices on both ends are positioned so that the distance between them is as short as possible.

[0009] In the above configuration, the bearing device may more specifically have a bearing box (housing), bearing components arranged inside the housing, and / or sealing components that prevent leakage of grease or other oils applied to the bearing components. A part of the bearing box, a part of the bearing components, or the sealing components may fit into the concave recess in the end surface of the body portion. [Effects of the Invention]

[0010] The roll structure of the present invention described above makes it possible to reduce deflection due to a load from a thin film or the like acting on the barrel portion without providing an end portion with a bending mechanism that applies a bending load to bend the barrel portion in the opposite direction to the deflection due to the load from the thin film or the like acting on the barrel portion. Furthermore, since the configuration of the present invention does not actively bend the barrel portion, the central axis of the end portion does not tilt relative to the central axis of the bearing device. Applying a bending load between the bearing device and the end portion does not tilt the end portion, which prevents increased friction between the bearing device and the end portion. Therefore, heat generated by such friction is also reduced. According to the present invention, with a simple structure, deflection due to a load from a thin film or the like acting on the barrel portion is reduced, and a reduction in the pressing force on the thin film or the like being fed along the rotation direction from the barrel portion is suppressed, which is expected to prevent problems with the compression and feeding of the thin film or the like.

[0011] Other objects and advantages of the present invention will become apparent from the following description of preferred embodiments of the invention. [Brief explanation of the drawings]

[0012] [Figure 1] 1(A) and (B) are schematic side views of a conventional roll structure in which both ends are rotatably supported by bearings. (A) shows a state in which no load is applied, and (B) shows a state in which a load perpendicular to the central axis is applied. Figures 1(C) and (D) are schematic side views of a roll structure in which both ends are rotatably supported by bearings according to this embodiment. (C) shows a state in which no load is applied, and (D) shows a state in which a load perpendicular to the central axis is applied. [Figure 2] FIG. 2 is a schematic diagram illustrating the relationship between the load acting on the roll structure and the deflection. [Figure 3] 3(A) and (B) are a schematic diagram (upper diagram) of a roll structure used in a simulation to calculate deflection when a load perpendicular to the central axis is applied to the roll structure, and a graph (lower diagram) showing the amount of deflection along the axial direction. (A) is a conventional example, and (B) is an example according to this embodiment. [Figure 4] 4(A) and (B) are schematic diagrams of an embodiment of the roll structure according to this embodiment. [Explanation of symbols]

[0013] 1...roll structure, 2...body portion, 2a...end surface of body portion, 2b...recess on end surface of body portion, 3...end portion, 4...bearing device, F...load BEST MODE FOR CARRYING OUT THE INVENTION

[0014] The present invention will now be described in detail with reference to some preferred embodiments thereof with reference to the accompanying drawings, in which like reference numerals indicate like parts.

[0015] Schematic configuration of the roll structure As shown in FIG. 1A, a roll structure 1, such as a press roll in a roll press or the like, has a cylindrical barrel portion 2. End portions 3 (smaller in diameter than the barrel portion 2) extending outward from both end surfaces 2a of the barrel portion 2 and centering around a central axis o are rotatably supported by bearing devices 4. As the roll structure 1 rotates, it presses a thin film or the like (not shown) against the surface of the barrel portion 2 along the rotational direction and delivers the thin film or the like. In this configuration, when the surface of the barrel portion 2 presses the thin film or the like, a reaction force, as shown in FIG. 1B, applies a load F to the barrel portion 2 in a direction perpendicular to the central axis, resulting in a deflection b in the direction of the load F (the deflection of the barrel portion 2 in FIG. 1B is exaggerated). As mentioned above, if the deflection of the barrel portion 2 is large, it will be difficult to sufficiently press and deliver the thin film or the like. Therefore, it is preferable that the deflection of the barrel portion 2 be as small as possible.

[0016] Regarding the deflection of the body part 2, as shown in Figure 2, when a distributed load w perpendicular to the central axis o acts on a cylinder (roll structure) 1 supported by supports (bearings) 4 at both ends, the deflection b of the center of the cylinder 1 is expressed as follows: b=5wL 4 / (384EI) (L is the distance between supports, E is Young's modulus, and I is the second moment of area) Therefore, the deflection b can be reduced by reducing the distance L between the supporting points, that is, the distance L between the supporting positions of the bearings 4 at both ends.

[0017] Therefore, in this embodiment, as schematically illustrated in Fig. 1(C), without changing the axial length L0 of the barrel portion 2, a concave recess 2b is formed in the end surface 2a of the barrel portion 2, and at least a portion of the bearing device 4 in the end portion 3 is fitted into the recess 2b, so that the bearing device 4 is moved closer to the center of the barrel portion 2 than in the case of the conventional roll structure 1 (Fig. 1(A)). According to this configuration, the inter-bearing distance L2 in the roll structure (Fig. 1(C)) of this embodiment is shorter than the inter-bearing distance L1 in the conventional roll structure 1 (Fig. 1(A)). Therefore, in the roll structure 1 (Fig. 1(C)) of this embodiment, when the barrel portion 2 receives a load F, the deflection b2 is reduced compared to the deflection b1 in the conventional roll structure 1 (Fig. 1(A)).

[0018] Computational Experiments The reduction in deflection in the roll structure 1 constructed according to the teachings of this embodiment was also confirmed in a calculation simulation experiment illustrated in FIG. 3. In the experiment, both ends of the roll structure 1 of the barrel portion 2 having an axial length of 490 mm as illustrated in the upper diagrams of FIGS. 3(A) and (B) were supported by bearing devices 4, and the deflection was calculated when 490 kN was applied to the entire barrel portion 2. In the conventional example, as shown in FIG. 3(A), the bearing device 4 was in contact with the end face of the barrel portion 2 where no recess was provided, while in the example of this embodiment, as shown in FIG. 3(B), the bearing device 4 was in contact with the end face of the barrel portion 2 where a recess was provided. As a result, as shown in the lower diagram of the same figure, in the case of the conventional structure of FIG. 3(A), the maximum deflection at the center of the barrel portion 2 was 5.622 μm, while in the case of the structure of this embodiment of FIG. 3(B), the maximum deflection at the center of the barrel portion 2 was 3.752 μm. This shows that, according to the teachings of this embodiment, by providing a recess 2b on the end face 2a of the body portion 2 and making at least a portion of the bearing device 4 fit into the recess 2b, the distance between the bearing devices 4 at both ends can be reduced without changing the axial length of the body portion 2, thereby reducing the amount of deflection under load.

[0019] Implementation The configuration of providing recesses in the end surfaces of the barrel portion of the roll structure according to this embodiment to reduce the distance between the bearing devices 4 at both ends may be applied when using bearing devices with various configurations. For example, as schematically illustrated in FIG. 4(A), in a case where the bearing device 4 has a bearing component 4b housed inside a housing (bearing box) 4a and the barrel portion 2 side of the housing 4a is open, a portion of the bearing component 4b may be inserted into the recess 2b in the end surface 2a of the barrel portion 2 and directly face the wall of the end surface 2a, and the bearing component 4b may be positioned as close to the center of the barrel portion 2 as possible. Furthermore, in a case where a sealing component 4c for preventing leakage of oils and grease applied to the bearing component is provided on the barrel portion 2 side of the housing 4a of the bearing device 4, the sealing component 4c may be inserted into the recess 2b in the end surface 2a of the barrel portion 2 and directly face the wall of the end surface 2a, and the bearing component 4b may be positioned as close to the center of the barrel portion 2 as possible.

[0020] Thus, according to the configuration of this embodiment, by providing a recess in the end surface of the barrel portion of the roll structure and having at least a part of the bearing device inserted into the recess, the distance between the bearings that rotatably support the roll structure at both ends of the barrel portion can be reduced, thereby making it possible to reduce deflection due to load. The configuration of this embodiment may be applied to any roll structure.

[0021] The above description has been made in relation to the embodiments of the present invention, but it will be apparent that many modifications and changes will be readily apparent to those skilled in the art, and the present invention is not limited to the above-described exemplary embodiments, but can be applied to various devices without departing from the concept of the present invention.

Claims

[Claim 1] A roll structure having a cylindrical body portion and end portions extending outward in the direction of the central axis from each of the end faces on both sides thereof, the end portions having a smaller shaft diameter than the body portion, and each of the end portions being rotatably supported by a bearing device, and configured to rotate around the central axis while pressing and feeding a thin film or thin plate with the surface of the body portion along the direction of rotation, wherein the end faces of the body portion are recessed in a concave shape on the outer periphery of the end portions, and at least a part of the bearing device is fitted into the concave recess.

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