JP2009019711A - Bearing structure for coating roll and application device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To materialize high rotation accuracy without variation of rotary axis center of a coating roll even if the coating roll bends or external force in a direction other than gravity direction acts on the coating roll. <P>SOLUTION: This bearing structure is provided with a hydraulic static pressure bearing 26 rotatably supporting a rotary shaft 22 of a roll 14 and a plain bearing 27 supporting the hydraulic static pressure bearing 26 and allowing inclination of the hydraulic static pressure bearing 26 as to follow only deflection in the gravity direction of the roll 14. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to a coating roll bearing structure and a coating apparatus, and more particularly to a coating roll bearing structure in a coating apparatus that uniformly forms a wide coating surface.

  Conventionally, various types of coating roll apparatuses have been proposed (for example, Patent Document 1). Each of these coating roll apparatuses applies a coating solution while guiding a film having a relatively small width.

  By the way, with an increase in the area of functional films (for example, optical compensation films, antireflection films, etc.) used for liquid crystal displays and the like, the film width increases, and a wide coating roll apparatus is required.

  However, in a wide coating roll apparatus, axial deflection due to the weight of the coating roll (hereinafter, also simply referred to as “roll”) increases, and the moment on the bearing portion increases, resulting in roll runout during rotation. Moreover, the load to a bearing part increases with the increase in the roll weight accompanying lengthening of a roll. As a result, there has been a problem that the rotational accuracy of the roll is remarkably lowered and the coating film thickness applied to the film becomes non-uniform.

  On the other hand, for example, in Patent Document 2, a bearing with a self-aligning mechanism (roller bearing) is used as a mechanism for rotating the roll. In order to compensate for the low rotational accuracy of the self-aligning mechanism-equipped bearing, a gas bearing outer ring is fixed inside the roll, and a gas bearing support shaft is provided inside the gas bearing outer ring. Thereby, the torque nonuniformity accompanying roll rotation is suppressed.

Patent Document 3 proposes a bearing structure in which a roll is fixed to an inner ring of an angular bearing, an outer ring of the angular bearing is fixed to an inner peripheral surface, and the outer peripheral surface is fitted with a housing having a spherical body. According to this, the rotation of the roll is made free regardless of the gravity direction or the horizontal direction. In addition, it is said that high rotational accuracy can be realized because there is no play in the axial direction of the angular bearing.
JP 2002-336756 A JP-A-6-221325 JP 2006-349100 A

  However, in the methods disclosed in Patent Documents 2 and 3, since rolling bearings are used, the bearing structure is likely to be a source of vibration and external vibrations are also easily transmitted. For this reason, there has been a problem that the dynamic characteristics of the bearing are low and disturbances such as vibration are easily transmitted to the film.

  Furthermore, the above-mentioned Patent Document 3 using a spherical housing has the following problems.

  (1) The clearance between the roll and the coating head varies. Specifically, FIG. 6 is a top view when the roll 5 is set on the conventional bearing member 2, but as shown in FIG. 6, the bearing member 2 aligns also in the conveyance direction of the film 3. . That is, since the outer peripheral surface of the inner ring 4 constituting the spherical housing is spherical in the film transport direction, it tilts in the film transport direction (Y direction) as indicated by the arrow. For this reason, when an external force in the horizontal direction (for example, tension in the film transport direction) is applied to the roll 5, the clearance between the roll 5 and the coating head 6 varies greatly to form a coating surface with a uniform film thickness. It becomes difficult.

  (2) When the roll is aligned with the spherical housing, the point contact increases due to the structure, so that the dynamic characteristics of the bearing portion deteriorates and vibrations occur. If this vibration is transmitted to the roll, there is a possibility that the coating performance on the film is lowered.

  (3) The spherical surface of the spherical housing has low processing accuracy and high cost.

  Furthermore, in order to perform high-precision thin-layer coating in the production of functional films, high rotational accuracy of 1 μm or less is required as a roll.

  The present invention was made in view of such circumstances, even if the coating roll bends or an external force other than the direction of gravity is applied to the coating roll, the rotation axis of the coating roll does not fluctuate, An object of the present invention is to provide a bearing structure for a coating roll that can achieve high rotational accuracy.

  According to a first aspect of the present invention, in order to achieve the above object, a first bearing portion that rotatably supports a rotating shaft of a coating roll, a first bearing portion that supports the first bearing portion, and a deflection in the gravity direction of the coating roll. A coating roll bearing structure comprising: a second bearing portion that allows tilting of the first bearing portion so as to follow only.

  According to the first aspect of the invention, the second bearing portion that allows the tilting of the first bearing portion is provided so as to follow only the bending of the coating roll in the gravity direction. As a result, even if the coating roll is bent, the roll does not shake during rotation or increases the load on the bearing, and rotates while forming a constant rotation axis in a bent state. Even if an external force other than the direction of gravity is applied to the coating roll, the rotation axis of the coating roll does not fluctuate. Thereby, high rotation accuracy is realizable.

  Although it does not specifically limit as a 1st bearing part, For example, a hydraulic hydrostatic bearing etc. can be used preferably. In addition, when there is little disturbance such as vibration entering from the outside, a highly accurate ball bearing system or roller bearing system can be adopted. Further, when the influence of the load or moment applied to the bearing is small, such as the weight of the coating roll is small, a pneumatic bearing method using air pressure, a magnetic bearing method using magnetic force, or the like can be employed.

  Claim 2 is the slide bearing part inner ring according to claim 1, wherein the second bearing part is provided on an outer periphery of the first bearing part, and supports the first bearing part on an inner peripheral surface, and the sliding bearing part inner ring. And a sliding bearing part outer ring that slidably supports the outer circumferential surface of the inner ring.

  A third aspect of the present invention provides the inner ring of the slide bearing portion according to the second aspect, wherein a pair of upper and lower outer peripheral surfaces facing each other forms an arcuate convex curved surface along the axial direction of the coating roll and A pair of outer peripheral surfaces opposed to each other are formed in a partially cylindrical shape, and the slide bearing portion outer ring has a pair of upper and lower inner peripheral surfaces along the axial direction of the coating roll. A pair of inner peripheral surfaces that form an arcuate concave curved surface that is in contact with the pair of outer peripheral surfaces and that oppose left and right with the axial direction as a center are a pair of outer peripheral surfaces that oppose the left and right sides of the sliding bearing inner ring. It has a partial cylindrical space with a flat surface in contact with it.

  According to the third aspect, since the side surfaces of the sliding bearing inner ring and the sliding bearing outer ring constituting the second bearing portion that face the left and right with respect to the axial direction of the coating roll are made flat, the second bearing portion The tilting in the left-right direction can be restricted. In addition, since the two outer peripheral surfaces facing the top and bottom of the inner ring of the sliding bearing portion form an arcuate convex curved surface, the coating roll can be allowed to tilt in the axial direction.

  Thereby, since the point contact part can be reduced as compared with the conventional bearing while ensuring the degree of freedom necessary for alignment, alignment can be performed with improved dynamic characteristics of the bearing. Further, since the accuracy of the curved surface processing is higher than that of the conventional spherical type slide bearing, even if the inner diameter of the slide bearing portion and the outer ring of the slide bearing portion become large, both can be accurately processed. Therefore, the alignment can be made highly accurate and the cost can be reduced.

  A fourth aspect of the present invention is characterized in that, in the third aspect, a radius of curvature R of the arcuate convex curved surface is 0.8 to 2 times an inner diameter d of the inner ring of the sliding bearing portion.

  If the radius of curvature of the arc-shaped convex curved surface is too small, the rigidity required to support the coating roll will be lowered due to the structure. If the radius of curvature is too large, sufficient alignment cannot be obtained. Neither is preferred. According to claim 4, the radius of curvature of the arc-shaped convex curved surface is 0.8 to 2 times (about 40 to 500 mm) the inner diameter d (about 50 to 250 mm) of the inner ring of the sliding bearing portion. Such a problem can be suppressed.

  A fifth aspect of the present invention is the third or fourth aspect, wherein the ratio B / R between the width B between the planes facing the left and right and the radius of curvature R is 1 to 5 in the outer peripheral surface of the inner ring of the sliding bearing portion. It is characterized by.

  According to the fifth aspect, even if a force other than the direction of gravity acts on the inner ring of the sliding bearing, the position of the inner ring of the sliding bearing becomes stable with respect to the outer ring of the sliding bearing, thereby reducing the dynamic characteristics of the inner ring of the sliding bearing. High alignment can be demonstrated without any problems. That is, if the B / R ratio is less than 1, the dynamic characteristics of the inner ring of the sliding bearing portion are likely to deteriorate, and if the B / R ratio exceeds 5, the weight of the inner ring of the sliding bearing portion increases, making smooth alignment difficult. For this reason, the B / R ratio is preferably about 1 to 5.

  According to a sixth aspect of the present invention, in any one of the first to fifth aspects, the pair of first bearing portions are hydraulic hydrostatic bearings.

  According to the sixth aspect of the present invention, the hydrostatic bearing system that exhibits high vibration damping, high rotational accuracy, high load capacity, etc. is adopted as the bearing system for supporting the coating roll. Can be improved. Further, in the first bearing portion that supports the long coating roll, it is possible to prevent galling (contact) between the outer peripheral surface of the rotating shaft and the inner peripheral surface of the first bearing portion, which are a concern.

According to a seventh aspect of the present invention, in the sixth aspect, the measuring means for measuring the temperature of the lubricating oil of the hydraulic hydrostatic bearing, and the temperature control means for controlling the lubricating oil to a predetermined temperature based on the result of the measuring means, ,
It is provided with.

  In order to support a coating roll having a large width or weight, high bearing rigidity is required. For this reason, the oil supply pressure in the hydraulic hydrostatic bearing increases, and the lubricating oil easily generates heat. Even if the temperature of the lubricating oil varies within a range of ± several degrees, the bearing performance is affected, so that the temperature control of the lubricating oil is important. According to the seventh aspect, since the temperature of the lubricating oil is monitored and controlled so that the lubricating oil reaches a predetermined temperature, the performance of the bearing can be maintained stably.

  An eighth aspect is characterized in that, in any one of the first to seventh aspects, an effective surface length of the coating roll is 3000 mm or less.

  The coating roll having such a large width increases the axial deflection due to its own weight. According to the ninth aspect, since the effective surface length of the coating roll is 3000 mm or less, the deflection amount of the coating roll can be made constant or less (50 μm or less).

  According to a ninth aspect of the present invention, in order to achieve the above object, at least one of a pair of bearing members provided on both ends of the rotary shaft of the coating roll and rotatably supporting the rotary shaft is the first to eighth aspects. The bearing structure of the coating roll characterized by having the bearing structure of any one of these.

  A tenth aspect of the present invention is the ninth aspect, wherein each of the pair of bearing members has the bearing structure according to any one of the first to eighth aspects, and one of the pair of bearing members has a first bearing portion. It is characterized by being supported by a thrust bearing.

  If the coating roll is simply supported by the journal type hydrostatic bearing, the movement of the rotating shaft in the thrust direction becomes free. For this reason, there is a method of supporting the thrust direction at both ends of the coating roll as a bearing mechanism for restricting the movement of the coating roll in the thrust direction. However, when thermal expansion in the axial direction of the coating roll due to heat generation of the lubricating oil occurs, there is no play in the axial direction, and there is a risk of deformation due to a compressive load. According to the tenth aspect, since the thrust bearing is provided on only one of the coating rolls, the above-described problems can be suppressed.

  According to an eleventh aspect of the present invention, in order to achieve the above object, a coating liquid bridge is formed in a clearance between a coating head and a strip-shaped film wound around a coating roll and traveling in the horizontal direction, and the coating is performed. In an extrusion-type coating apparatus that coats the film with a coating liquid discharged from a head, at least one of a pair of bearing members that rotatably support a rotating shaft of the coating roll is any one of claims 1 to 8. A coating apparatus comprising the bearing structure according to item 1 is provided.

  According to the eleventh aspect, in such a coating apparatus, the rotation axis of the coating roll does not fluctuate in the film conveyance direction. For this reason, a uniform clearance can be formed between the coating roll around which the film is wound and the coating head, and the coating liquid can be uniformly coated. The coating roll includes a backup roll.

  According to the present invention, even if the coating roll is bent or an external force other than the gravity direction is applied to the coating roll, the rotation axis of the coating roll does not fluctuate and high rotation accuracy can be realized.

  Hereinafter, preferred embodiments of a coating roll bearing structure and a coating apparatus according to the present invention will be described in detail with reference to the accompanying drawings.

  FIG. 1 is a perspective view for explaining the outline of a coating apparatus having a coating roll bearing structure according to the present invention. Among these, FIG. 1 (A) is a figure which shows the principal part of a coating device, and FIG. 1 (B) is a figure which shows the structural member of a bearing member.

  As shown in FIG. 1, a coating device 10 is a device that applies a coating solution to a continuously running film, and mainly a backup roll 14 (hereinafter simply referred to as “roll 14”) around which the film 12 is wound. And an extrusion-type coating head 16 disposed with a predetermined clearance with respect to the roll 14. Hereinafter, the axial direction of the roll 14 is the X direction, and the left and right direction (the direction perpendicular to the axial direction or the film transport direction) is the Y direction and the vertical direction (the direction of gravity) is the axial direction of the roll 14 The Z direction is used, and both include the plus side and the minus side.

  A pocket 18 is formed in the width direction of the film 12 inside the extrusion type coating head 16. The pocket 18 communicates with the slit opening 20 a at the tip (lip) of the coating head 16 via the slit 20. The slit opening 20 a is formed in an elongated shape in the width direction of the film 12, and the width dimension is formed to be substantially equal to the width dimension of the film 12. Then, the coating liquid supplied to the pocket 18 via the supply path 17 by a coating liquid supply source (not shown) is discharged from the slit opening 20 a via the slit 20. Then, a coating solution bridge (bead) is formed in the clearance between the tip of the coating head 16 and the continuously running film 12, and the coating solution is transferred to the film 12. The application head 16 is supported by a support member (not shown).

  The roll 14 is formed to be wide enough to wind the film 12, and the rotating shafts 22 at both ends thereof are rotatably supported by bearing members 24 having the bearing structure according to the present invention.

  For example, the roll 14 used in the present invention is easily bent in the direction of gravity due to its own weight because the weight of the roll 14 is about 400 kg and the width is relatively large. When this bending occurs, the clearance distribution between the coating head 16 and the roll 14 becomes non-uniform. For this reason, in order to keep the clearance distribution between the coating head 16 and the roll 14 uniform, it is necessary to adjust the tip shape of the coating head 16 to the shape of the bent roll 14. The amount of error that appears during this adjustment is affected by the amount of deflection of the roll 14. Specifically, about 10% of the deflection amount of the roll 14 appears as a clearance adjustment error.

  Since the distribution accuracy of the clearance between the coating head 16 and the roll 14 is required to be 5 μm or less, the deflection amount of the roll 14 is preferably 50 μm or less, and the effective surface length L of the roll 14 is 3000 mm or less. It is preferable.

  However, even if the above adjustment is performed, the film 12 is wound around the roll 14 and conveyed in the horizontal direction. Therefore, due to fluctuations in the tension of the film 12 applied to the roll 14 and external vibration in the conveyance direction transmitted to the roll 14. The clearance between the coating head 16 and the roll 14 varies. Thereby, the film thickness distribution of a coating layer and the film width direction becomes non-uniform | heterogenous. For this reason, it is necessary to stably support (align) the roll 14 so as not to cause shaft runout (fluctuation of the rotational axis) while following the axial deflection of the roll 14.

  Therefore, in the present invention, the bearing member 24 is configured so as to eliminate alignment in the film conveyance direction (Y direction) and align only in the axial direction (X direction) of the roll 14. Hereinafter, the bearing member 24 which is a characteristic part of the present invention will be described.

  In the bearing member 24, a hydraulic hydrostatic bearing 26 (first bearing portion) that rotatably supports the rotating shaft 22 is disposed on the outer periphery of the rotating shaft 22 of the roll 14, and further on the outer periphery thereof is a hydraulic type. A slide bearing 27 (second bearing portion) that supports the hydrostatic bearing 26 and aligns the roll 14 is provided.

  The slide bearing 27 includes a slide bearing portion inner ring 28 and a slide bearing portion outer ring 30.

  As shown in FIG. 1B, the slide bearing portion inner ring 28 has two outer peripheral surfaces 28a, 28b facing the Z direction (vertical direction) of the slide bearing portion inner ring 28 in a convex curved surface having an arc shape in the X direction. The two outer peripheral surfaces 28c and 28d facing the Y direction (left and right with the axial direction as the center) are formed in a partially cylindrical shape that forms a plane.

  A slide bearing portion outer ring 30 that supports the slide bearing portion inner ring 28 is disposed on the outer periphery of the slide bearing portion inner ring 28, and is formed so as to accommodate the slide bearing portion inner ring 28. That is, the two inner peripheral surfaces 30a and 30b facing the Z direction (vertical direction) of the outer ring 30 form an arcuate concave curved surface in the X direction, and are opposed to the Y direction (left and right around the axial direction). The two inner peripheral surfaces 30c and 30d are flat (see FIG. 4 described later). As a result, the slide bearing inner ring 28 tilts only in the X direction and does not tilt in the Y direction. Therefore, the hydraulic hydrostatic bearing 26 that supports the rotating shaft 22 can be allowed to tilt only in the X direction and can not be tilted in the Y direction.

  If the radius of curvature R is too small, the outer peripheral surfaces 28a and 28b of the plain bearing portion inner ring 28 are structurally less rigid to support the roll 14, and if the radius of curvature R is too large, the alignment is reduced. For this reason, the curvature radius R of the outer peripheral surfaces 28a and 28b of the sliding bearing portion inner ring 28 is set to 0.8 to 2 times (about 40 to 500 mm) the inner diameter d (about 50 to 250 mm) of the sliding bearing portion inner ring 28. Is preferred.

  Of the outer peripheral surface of the sliding bearing inner ring 28, the ratio between the width B and the radius of curvature R between the two outer peripheral surfaces 28c, 28d facing in the Y direction (left and right with the axial direction as the center) (hereinafter referred to as "B / When the R ratio is less than 1, the dynamic characteristics of the sliding bearing inner ring 28 are likely to deteriorate, and when it exceeds 5, the weight of the sliding bearing inner ring 28 increases, and smooth alignment cannot be achieved. For this reason, it is preferable to make B / R ratio into 1-5.

  FIG. 2 is an enlarged cross-sectional view illustrating the internal configuration of the bearing member 24 having the bearing structure according to the present invention. The figure shows the bearing member 24 on the side where the thrust bearing is provided.

  As shown in FIG. 2, an outer peripheral member 32 of a hydraulic hydrostatic bearing 26 that rotatably supports the rotating shaft 22 is fixed to the inner peripheral surface of the slide bearing portion inner ring 28. It moves together. An oil supply groove 34 for supplying lubricating oil is provided in the circumferential direction on the inner peripheral surface of the slide bearing portion inner ring 28.

  A static pressure pocket 36 and an atmospheric pressure release groove 38 are formed along the circumferential direction and the axial direction between the inner wall surface of the hydraulic static pressure bearing 26 and the rotary shaft 22, and the static pressure pocket 36 and the atmospheric pressure are formed. The release groove 38 communicates with the outer peripheral surface of the rotating shaft 22 via a bearing metal member 40 in which a fine flow path is formed so that lubricating oil can pass. The atmospheric pressure release groove 38 is sealed by a seal member 42. Further, an oil supply port 44 is formed on the surface of the outer peripheral member 32 facing the oil supply groove 34, and the oil supply port 44 and the static pressure pocket 36 communicate with each other through an oil supply hole 46 formed in a fine channel shape. ing. The static pressure pockets 38 and 38 communicate with an oil drain hole 48 formed along the axial direction at the lower part in the direction of gravity, and the oil drain hole 48 communicates with an oil drain port 50.

  Thereby, the lubricating oil passes from the oil supply groove 34 formed in the circumferential direction through the oil supply port 44 and the oil supply hole 46, and the static pressure pocket 36, the bearing metal member 40 (circumferential fine flow path), and the atmospheric pressure. It is supplied to the release groove 38. The lubricating oil circulating through the static pressure pocket 36 and the atmospheric pressure release groove 38 is collected in the oil drain hole 48 and then discharged to the outside through the oil drain port 50.

  A lubricating oil supply source 52 for storing and supplying lubricating oil communicates with each of the oil supply groove 34 and the oil discharge port 50 through pipe lines 54a and 54b, and a lubricating oil circulation path 54 is formed. A thermometer 56 for measuring the temperature of the lubricating oil and a lubricating oil temperature control mechanism 58 are provided in the middle of the lubricating oil circulation path 54. In the thermometer 56, the temperature of the lubricating oil can be constantly monitored. The lubricating oil temperature control mechanism 58 controls the temperature of the lubricating oil to be a predetermined temperature using a temperature control device such as air cooling, water cooling, or a refrigerant method. Thereby, based on the temperature measurement result of the lubricating oil in the thermometer 56, the lubricating oil temperature control mechanism 58 controls the temperature of the lubricating oil to be a predetermined temperature.

  Inside the hydraulic hydrostatic bearing 26, a thrust bearing 60 is provided in a flange shape next to the atmospheric pressure release groove 38 on the side opposite to the roll 14. The thrust bearing 60 is rotatable together with the roll 14 while being fixed to the roll 14, and oil is applied to the circumferential side surface between the outer peripheral member 32 and the fixed member 62 fixed by the screw 64. A fine flow path that can be lubricated is formed. The lubricating oil that has flowed out of the atmospheric pressure release groove 38 passes through the fine flow path and lubricates to restrict the movement of the roll 14 in the axial direction. A rubbing seal 66 is provided on the roll 14 side of the hydraulic hydrostatic bearing 26 as necessary.

  The thrust bearing 60 is preferably provided on only one of the pair of bearing members 24. That is, when the lubricating oil generates heat, thermal expansion in the axial direction of the roll 14 occurs, but the amount of expansion increases as the roll becomes longer. If the thrust direction is supported at both ends of the roll 14, there is no play in the axial direction, and there is a risk of deformation due to a compressive load. Therefore, by providing the thrust bearing 60 on only one of the pair of bearing members 24 that support the roll 14, the above problems are suppressed.

  Next, the effect | action of this invention is demonstrated with reference to FIG.3 and FIG.4. FIG. 3 is an explanatory diagram for explaining how the roll bends in the direction of gravity, and FIG. 4 is an explanatory diagram for explaining the operation of the bearing member 24. Among these, FIG. 4 (A) is the figure which looked at the operation | movement in the coating device 10 from the front, and is sectional drawing in the gravity direction of the bearing member 24. FIG. FIG. 4B is a view of the operation of the coating apparatus 10 as viewed from above, and is a cross-sectional view of the bearing member 24 in the horizontal direction.

  First, the lubricating oil supply source 52 is operated to supply the lubricating oil from the oil supply groove 34 to the static pressure pocket 36 and the atmospheric pressure release groove 38 in the hydraulic hydrostatic bearing 26, and the oil discharge hole 48 and the oil discharge port 50. And is circulated to the lubricating oil supply source 52. The oil temperature and oil pressure at this time are set to appropriate values according to design conditions such as roll weight, rotation speed, and required rigidity value. Then, the roll 14 is rotated.

  As the roll 14 is rotated, as shown in FIG. 3, the roll 14 is bent in the direction of gravity by its own weight, and the rotation axis 14 </ b> A (dotted line) is shaken from the horizontal.

  At this time, as shown in FIG. 4A, in the bearing member 24, the inner ring 28 of the plain bearing portion tilts in the X direction following the bending of the roll 14 (see arrow). Therefore, even if the coating roll is bent, the roll does not shake during rotation or increases the load on the bearing, and rotates while forming a constant rotation axis in the bent state.

  When the state at this time is viewed from above, as shown in FIG. 4B, in the bearing member 24, the outer peripheral surface 28c of the sliding bearing inner ring 28 and the inner peripheral surface 30c of the outer ring 30 in the Y direction, Since the outer peripheral surface 28d of the sliding bearing portion inner ring 28 and the inner peripheral surface 30d of the sliding bearing portion outer ring 30 are in contact with each other on a plane, the sliding bearing portion inner ring 28 is stably fixed without tilting in the Y direction. .

  That is, even if the roll 14 is bent, the plain bearing portion inner ring 28 is tilted only in the X direction so as to follow the bending, and is not tilted in the Y direction. For this reason, the rotation axis 14A (dotted line) of the roll 14 does not fluctuate, and the roll 14 can be rotatably supported with high rotational accuracy. Further, the clearance distribution between the coating head 16 and the roll 14 can be made uniform.

  As described above, according to the present embodiment, it is possible to suppress the roll shake of the roll in the film conveyance direction and to achieve high rotation accuracy. Compared to conventional spherical type plain bearings, the partial cylindrical type slide bearing of the present invention has a higher accuracy of curved surface processing. Therefore, even if the inner diameter of the slide bearing part and the outer ring of the slide bearing part become larger, both of them can be combined. Processing can be performed with high accuracy. Therefore, the alignment can be made highly accurate and the cost can be reduced.

  In addition, as a film 12 used for this invention, well-known various films can be used. Generally, various known plastic films such as polyethylene terephthalate, polyethylene-2,6-naphthalate, cellulose diacetate, cellulose triacetate, cellulose acetate propionate, polyvinyl chloride, polyvinylidene chloride, polycarbonate, polyimide, polyamide, Paper, various laminated papers coated with or laminating α-polyolefins having 2 to 10 carbon atoms such as polyethylene, polypropylene, ethylene butene copolymer, etc., belt-like substrates such as metal foils such as aluminum, copper and tin And a composite material obtained by laminating these layers.

  As mentioned above, although preferable embodiment of the bearing structure of the roll concerning this invention was described, this invention is not limited to the said embodiment, Various aspects can be taken.

  For example, in each of the above embodiments, the hydrostatic hydrostatic bearing 26 that is reliable in high vibration damping, high rotational accuracy, high load capacity, and the like is employed as the first bearing portion that supports the rotating shaft 22. However, various bearings can be used. In addition, when there is little disturbance such as vibration entering from the outside, a highly accurate ball bearing system or roller bearing system can be adopted. Further, when the required load capacity is small and the influence of the moment is small, such as the weight of the roll is small, a pneumatic bearing method using air pressure, a magnetic bearing method using magnetic force, or the like can be adopted.

  In each said embodiment, although the bearing member 24 which has the bearing structure which concerns on this invention was arrange | positioned at the both ends of the roll 14, it is not limited to this, You may arrange | position to only one side. Also in this case, the same effect as described above can be obtained.

  Further, in the present embodiment, the bearing structure that supports the backup roll around which the film is wound in the coating apparatus using the extrusion type coating head has been described, but the present invention is not limited to this, for example, the roller is scraped up by the roll. It can also be used as a coating bar in a bar coating device that transfers a coating solution to a film.

  Examples of the present invention will be described below, but the present invention is not limited to these examples.

  The amount of deflection when the effective surface length of the roll 14 was changed was measured.

  In the roll 14 having a material of SCM and an outer diameter of 120 mm, the effective surface length in the width direction of the roll 14 was changed in the range of 1000 to 4000 mm. The amount of deflection of the roll 14 was measured with a laser displacement meter at a total of three points on both ends and the center of the roll effective surface. The result is shown in FIG.

  As shown in FIG. 5, when the effective surface length of the roll 14 exceeds 3000 mm, the amount of deflection increases proportionally, whereas when the effective surface length of the roll 14 falls below 3000 mm, the amount of deflection is 50 μm or less. It turned out to be relatively small.

  Further, from the viewpoint of alignment, the preferred size and shape of the sliding bearing inner ring 28 were examined.

  When the radius of curvature R of the outer peripheral surfaces 28a, 28b of the inner ring 28 is 100 mm, changing the width B between the two opposing outer peripheral surfaces 28c, 28d of the inner ring 28 can affect the alignment by the B / R ratio. evaluated. The alignment of the bearing was visually observed and evaluated according to the following criteria.

A: Alignment property is extremely high, ◯: Alignment property is high, △: Alignment property is slightly low, but there is no practical problem, ×: Alignment property is low Table 1 shows the results.

  As shown in Table 1, it was found that when the B / R ratio is 1 to 5, preferably 2 to 3, high alignment is exhibited without deteriorating dynamic characteristics. However, although both are at a level where there is no problem in practical use, when the B / R ratio is smaller than 1, the dynamic characteristics of the slide bearing inner ring 28 tend to be slightly lowered, and the B / R ratio is larger than 5. As a result, the weight of the inner ring 28 of the slide bearing portion increased, and a tendency that smooth alignment was difficult was observed.

  From the above, high alignment can be stably maintained by setting the ratio (B / R ratio) between the width B between the planes in the Y direction of the slide bearing inner ring 28 and the curvature radius R in the Z direction to 1 to 5. I understood.

It is a perspective view explaining the outline | summary of the coating device provided with the bearing structure of the coating roll which concerns on this invention. It is an expanded sectional view explaining the internal structure of the bearing member in FIG. It is explanatory drawing explaining a mode that a roll bends in a gravitational direction. It is explanatory drawing explaining the operation | movement in the coating device of FIG. It is a graph which shows the result of a present Example. It is the horizontal sectional view seen from the upper part of the bearing member provided with the conventional spherical type housing.

Explanation of symbols

  DESCRIPTION OF SYMBOLS 10 ... Coating apparatus, 12 ... Film, 14 ... Roll, 16 ... Coating head, 22 ... Rotating shaft, 24 ... Bearing member, 26 ... Hydraulic hydrostatic bearing, 27 ... Slide bearing, 28 ... Sliding bearing inner ring, 28a, 28b ... Outer peripheral surface of sliding bearing inner ring (Z direction), 28c, 28d ... Outer peripheral surface of sliding bearing inner ring (Y direction), 30: Outer bearing of sliding bearing, 30a, 30b ... Inner peripheral surface of sliding bearing outer ring ( Z direction), 30c, 30d ... inner peripheral surface of sliding bearing outer ring (Y direction), 36 ... static pressure pocket, 38 ... atmospheric pressure release groove, 56 ... thermometer, 58 ... lubricating oil temperature control mechanism, 60 ... thrust bearing

Claims (11)

A first bearing portion that rotatably supports the rotating shaft of the coating roll;
A second bearing portion that supports the first bearing portion and allows the tilting of the first bearing portion so as to follow only the bending in the gravity direction of the coating roll;
A bearing structure for a coating roll, comprising: The second bearing portion is
A slide bearing portion inner ring provided on an outer periphery of the first bearing portion and supporting the first bearing portion on an inner peripheral surface;
A slide bearing portion outer ring provided on the outer periphery of the slide bearing portion inner ring, and slidably supporting the outer peripheral surface of the inner ring;
The bearing structure for a coating roll according to claim 1, wherein the bearing structure is a sliding bearing comprising The inner ring of the sliding bearing portion has a pair of outer peripheral surfaces facing vertically forming an arcuate convex curved surface along the axial direction of the coating roll and a pair of outer peripheral surfaces facing left and right centering on the axial direction. Is formed in a partial cylindrical shape,
The sliding bearing portion outer ring has an arcuate concave curved surface in which a pair of upper and lower inner peripheral surfaces contact the pair of outer peripheral surfaces of the sliding bearing inner ring along the axial direction of the coating roll. The pair of inner peripheral surfaces opposed to the left and right with a direction as a center has a partially cylindrical space that forms a plane in contact with the pair of outer peripheral surfaces opposed to the left and right of the sliding bearing inner ring. The bearing structure of the coating roll of 2.   The bearing structure of the coating roll according to claim 3, wherein a radius of curvature R of the arcuate convex curved surface is 0.8 to 2 times an inner diameter d of the inner ring of the sliding bearing portion. Among the outer peripheral surfaces of the sliding bearing inner ring,
5. The coating roll bearing structure according to claim 3, wherein a ratio B / R between a width B between the left and right planes and the radius of curvature R is 1 to 5. 5.   The bearing structure for a coating roll according to any one of claims 1 to 5, wherein the first bearing portion is a hydraulic hydrostatic bearing. Measuring means for measuring the temperature of the lubricating oil of the hydraulic hydrostatic bearing;
Temperature control means for controlling the lubricating oil to a predetermined temperature based on the result of the measurement means;
The bearing structure of the coating roll according to claim 6, comprising:   The bearing surface structure of the coating roll according to any one of claims 1 to 7, wherein an effective surface length of the coating roll is 3000 mm or less.   The bearing structure according to any one of claims 1 to 8, wherein at least one of a pair of bearing members provided on both ends of the rotating shaft of the coating roll and rotatably supporting the rotating shaft has the bearing structure according to any one of claims 1 to 8. Bearing structure of coating roll.   Each of the pair of bearing members has the bearing structure according to any one of claims 1 to 8, and one first bearing portion of the pair of bearing members is supported by a thrust bearing. A bearing structure for a coating roll according to claim 9. An extrusion type in which a coating liquid bridge is formed in the clearance between the coating head and a strip-shaped film wound around a coating roll and running in the horizontal direction, and the coating liquid discharged from the coating head is applied to the film. In the coating device of
The coating apparatus according to any one of claims 1 to 8, wherein at least one of a pair of bearing members that rotatably support the rotating shaft of the coating roll has the bearing structure according to any one of claims 1 to 8.

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