JP2009014144A - Bearing device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a roll bearing unit, which can be applied even to a portion having a large radial load in a continuous casting machine guide roll in a layout-free manner. <P>SOLUTION: When a radial load is applied from an ingot to a roller 4, it is supported by a cylindrical roller bearing. At that time, when a thrust load which acts also in the axial direction is given, for example, to the left in Fig. 3, movement of the roller to the left can be limited since a flange part 12e of an inner ring 12b of a right cylindrical roller bearing 12 abuts on the outer end of a cylindrical roller 12c to support the thrust load. When the thrust load is applied to the right, movement of the roller 4 to the right can be limited since a flange part 12e of an inner ring 12b of a left cylindrical roller bearing 12 abuts on the outer end of the cylindrical roller 12c to support the thrust load. Accordingly, the thrust load can be supported by a pair of cylindrical roller bearings 12, and the flexibility of layout can be extended without the concept of fixed side or free side. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to a bearing device, and more particularly to a bearing device suitable for supporting a rolling roller of a steel facility.

  At the steelworks, the finished steel is sent to the casting process. Slabs, blooms, billets, etc. are often cast in a continuous casting machine that directly produces billets from molten steel. The outline of the continuous casting equipment is as follows. First, molten steel is poured from the ladle into the tundish, and then poured into the mold from the top. Cooling water is sprayed on the surface of the slab, and the surface layer portion is sequentially fed backward by a plurality of guide rolls arranged continuously toward the lower side of the mold while solidifying gradually. After that, it is cut into a predetermined length by a cutting device to be a predetermined product size and conveyed to the next process.

  Since the roll used in the continuous casting equipment as described above is subjected to an excessive radial load from the slab and bends, a self-aligning roller bearing having a centering property is used as a bearing device for supporting the end of the roll. Often used.

  In addition, the bearing device that holds one end of the roll is fixed (fixed side) in order to cope with the thermal expansion of the roll caused by heating the roll from the hot slab and to position the roll in the axial direction. In general, a bearing device that supports the other end of the roll is used as a so-called free state (free side) in order to allow relative displacement in the axial direction between the roll and the outer ring.

Since the self-aligning roller bearing as shown in Patent Document 1 has a function of supporting a high load and a thrust load while supporting a heavy load, it is widely used as a support for a roll of steel equipment regardless of a fixed side or a free side. It is used.
JP 2002-5156 A JP-A-8-238549 JP 63-40623 A

  The bearings for guide rolls are not only subjected to severe loads from the slab through the roll, but also the surrounding environment is a hot and humid environment covered with water vapor because the cooling water is sprayed on the red slab. It is in. For this reason, deterioration of the seal provided in the axle box also proceeds, and water often enters the bearing through the seal. For this reason, the inside of the bearing tends to be poorly lubricated.

  Spherical roller bearings, which have been widely adopted under such severe usage conditions, generate minute slips that occur geometrically in bearings called differential slides or spin slides, and therefore the lubrication state is particularly high. When it is bad, abnormal wear progresses, and then a problem often occurs where peeling occurs early.

  The self-aligning roller bearing as shown in Patent Document 1 has a large feature that allows inclination, but has the above-mentioned problem of bearing damage. On the other hand, general cylindrical roller bearings can be designed with a larger load capacity than spherical roller bearings, and there is no problem with wear because there is no differential sliding or spin sliding. However, there is a problem that a large roll cannot be supported.

  On the other hand, as shown in Patent Document 2, a bearing device in which a centering ring is disposed between the outer ring of the cylindrical roller bearing and the housing, and the outer ring can be inclined with respect to the housing according to the deflection of the roll. Has been developed.

  However, the present bearing device has a problem that it cannot be used on the fixed side of the roll because the inner ring portion can be arbitrarily displaced in the axial direction. Accordingly, a roll unit structure in which a roller bearing as shown in Patent Document 2 is set on the free side and a self-aligning roller bearing is set on the fixed side is often used. In addition, as for the guide rolls of continuous casting machines, roll units with different bearings as fixed and free bearings at both ends of a single roll have been used for a long time. The structure of split-type rolls in which two to three short rolls are arranged in a row is increasing. A layout diagram of the 1, 2, 3 split roll arrangement is shown in FIGS. 2 (a), 2 (b), and 2 (c).

  In the case of such split-type rolls, it is known that there is a large variation in load sharing due to the arrangement of the bearings that support the slab and each roll end, and especially the load of the bearings arranged near the center of the different pieces. Is known to be severe.

  As the arrangement of bearings composed of two rolls, as a countermeasure for the central part where the bearing load is severe, as shown in Patent Document 2, a self-aligning roller bearing is used on the fixed side and a cylindrical roller bearing is used on the free side. Measures to place each on the free side have been devised and put into practical use.

However, in the case of a three-part roll, since the load of the roll arranged in the middle becomes a severe load sharing at both ends, in the roll unit structure in which the self-aligning roller bearing is combined on the fixed side and the cylindrical roller bearing on the free side, There is a risk that the spherical roller bearing on the fixed side may cause damage due to wear for the reasons described above, and it may be difficult to take countermeasures only by arranging the rolls as shown in Patent Document 2.

  As described above, in the case of a roll unit in a split roll, since the load sharing differs depending on the part, there is a problem that a design that fully considers the bearing type and arrangement of the roll bearing unit is necessary and the layout design is complicated.

  Furthermore, because the bearing type is different on the fixed side and the free side, the structure of the surrounding parts is also different, and the parts around the housing and bearing cannot be shared, resulting in high part costs, poor maintainability, and problems in parts management. Arise.

  In view of the problems of the prior art, the present invention originally has a structure of a roll bearing unit in the design of a continuous casting facility that is sought, and there is no restriction on the arrangement on the fixed side and the free side, and the number of divisions of the roll The present invention is not limited to providing a roll bearing unit that can be layout-free.

The bearing device of the present invention is used in a continuous casting facility, and is a bearing device that rotatably supports an end of a roll with respect to a housing,
An outer ring that is supported by the housing and integrally formed on both ends in the axial direction with flanges extending radially inward;
An inner ring that supports the roll and has a flange that extends radially outward on one end side in the axial direction;
And a plurality of cylindrical rollers arranged between the outer ring and the inner ring.

  As described above, conventionally, the slab has been rolled with one roll having a length exceeding the width of the slab, but in recent years, a split roll structure using a plurality of rolls smaller than the width of the slab. Has been adopted. In such a case, for example, in a two-part roll structure, the bending of the roll is slightly less than that of a single roll, but the load sharing differs depending on the part while allowing a slight inclination. There is a demand to adopt cylindrical roller bearings having a heart function and a large load capacity at both ends of the roll.

  On the other hand, in the three-part roll structure, the flexure of the roll due to the shortening of the total roll length is significantly reduced, so the load capacity is designed to be larger by using a space where the aligning ring is eliminated on the free side and the fixed side. There is a demand to use a general cylindrical roller bearing type.

  Here, in Patent Document 2 and a general cylindrical roller bearing type having no aligning ring, it can be used for the free side and can smoothly release the elongation in the axial direction due to the thermal expansion of the roll, but in the axial direction of the roll. Since the thrust force cannot be supported while the movement is restricted, it cannot be used on the fixed side.

  On the other hand, as shown in Patent Document 3 (Japanese Patent Laid-Open No. 63-40623), a structure in which a flange is provided at the end of the inner ring to support the thrust force while restricting the axial position of the inner ring for the fixed side, etc. However, there is a problem that the object of the present invention in which the fixed side bearing and the free side bearing have a common specification cannot be achieved.

  According to the bearing device of the present invention, since the flange extending outward in the radial direction is integrally formed on the inner ring only on one end side in the axial direction, it is held by the flange of the outer ring. The cylindrical roller thus made can support a thrust load in one direction by coming into contact with the flange portion of the inner ring. Therefore, in such a case, the bearing device of the present invention can be arranged on the fixed side of the roll. On the other hand, when a thrust load is received in the other direction, since the flange portion is not provided, relative displacement in the axial direction between the cylindrical roller and the inner ring is allowed. Therefore, in such a case, the bearing device of the present invention also has a function on the free side of the roll.

  That is, the bearing device of the present invention can use the same bearing device on both the fixed side and the free side of the roll. While the load capacity can be increased by using the cylindrical roller bearing, the layout-free roll arrangement design can be performed, and the number of parts and the cost can be reduced.

  If the flange of the inner ring is arranged on the outer side in the axial direction of the roll, for example, when the roll receives a thrust load to the left in the axial direction, this is supported by the flange of the inner ring in the bearing device on the left can do. On the other hand, when the said roll receives the thrust load to the axial direction right side, this can be supported by the collar part of the inner ring | wheel in the right side bearing apparatus. That is, it is possible to support thrust loads in both directions by reversing and using the same bearing device. Even if the roll expands due to thermal expansion, the inner ring rods arranged on both outer sides of the roll move in directions away from the roller end faces, so that smooth axial elongation is not hindered. Thereby, the concept of the fixed side or the free side of the roll becomes unnecessary, and the degree of freedom of the layout of the bearing device is greatly improved.

  An outer peripheral surface of the outer ring is a spherical surface, and an alignment ring having an inner peripheral surface corresponding to the outer peripheral surface of the outer ring is disposed between the outer ring and the housing to support a roll having a large deflection. It is preferable to do.

  Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings. FIG. 1 is a perspective view schematically showing a continuous casting facility using the bearing device according to the present embodiment. In the continuous casting facility shown in FIG. 1, the roller unit having any one of the arrangements shown in FIGS. 2 (a) to 2 (c) can be used.

  In FIG. 1, the molten slab FE is supplied from the upper introduction part 1, and is discharged | emitted in plate shape toward the vertical direction from the discharge part 2 made into two rows. The plate-shaped slab FE passes between the roller units 3 arranged to face each other, and is adjusted so that the plate thickness is gradually adjusted and gradually becomes horizontal by the rollers. The roller units 3 arranged on both sides of the slab FE are shielded by the chamber 9 as schematically shown by dotted lines, and the interior thereof is exposed to the high temperature of the slab FE and water for cooling. Environmental conditions.

  The roller unit 3 includes a segment composed of rollers (also referred to as guide rolls) 4 and 4 ′ for rolling the slab FE and bearing devices 10 and 10 ′ that support both ends of the rollers 4 and 4 ′. Here, for example, as shown in FIGS. 2 (a) to 2 (c), a pair of roller units 3 formed by combining segments of five or six rollers are arranged facing both sides of the slab FE. ing. The roller 4 'shown in FIG. 2 (a) is a segment that is longer than the width of the slab and is composed of one roll. The roller 4 shown in FIG. 2 (b) is a segment unit composed of two pieces whose overall length is shorter than the width of the slab. The roller 4 shown in FIG. 2 (c) is a segment unit composed of three pieces having a total length shorter than the width of the slab. As will be described later, in the present embodiment, any part may be combined with various roll arrangements having different roll lengths.

  FIG. 3 is a cross-sectional view of the bearing devices 10 and 10 that support one short roller 4 for rolling the slab FE. In the present embodiment, the same bearing devices 10 and 10 are used, but are used in an inverted manner, and therefore only one of them will be described. In FIG. 3, the roller 4 includes a first cylindrical portion 4 b, a second cylindrical portion 4 c, which are smaller in diameter than the rolled portion 4 a and coaxially arranged on both sides in the axial direction of the rolled portion 4 a for rolling the slab FE. The third cylindrical portion 4d is provided in this order from the rolling portion 4a side.

  In FIG. 3, a cylindrical portion 11 a and a seal holding portion 11 b are formed coaxially inside the housing main body 11 whose lower surface is fixed. A cylindrical roller bearing 12 is disposed in the cylindrical portion 11a. A seal 13 is disposed on the seal holding portion 11b, and its lip abuts on the outer periphery of the labyrinth ring 14 fitted to the first cylindrical portion 4b to seal it. The labyrinth ring 14 has a substantially U-shaped circumferential cross section, and forms a labyrinth seal as a non-contact seal by being combined with a correspondingly shaped housing body 11 with a minute gap. However, the seal structure is not limited to this.

  FIG. 4 is an enlarged view of the cylindrical roller bearing 12. 4, the cylindrical roller bearing 12 is disposed between an outer ring 12a fitted to the inner periphery of the housing body 11, an inner ring 12b fitted to the second cylindrical portion 4c of the roller 4, and the outer ring 12a and the inner ring 12b. A plurality of cylindrical rollers 12c. The outer ring 12a is formed by integrally forming flanges 12d and 12d extending inward in the radial direction at both ends in the axial direction so as to sandwich the cylindrical roller 12c. Further, the inner ring 12b is integrally formed with a flange 12e extending outward in the radial direction only at one end in the axial direction (here, the end closer to the outside of the roller 4 with respect to the cylindrical roller 12c). It becomes. A slight gap may be provided between 12e and 12c. Note that the outer periphery of the end of the inner ring 12b where the flange portion is not provided is a tapered surface 12g that decreases in diameter toward the outer side, so as to suppress catching or the like when the cylindrical roller 12c is inserted. Yes.

  In FIG. 3, an annular member 15 is fitted and disposed on the outer periphery of the third cylindrical portion 4 d of the housing body 11 so as to abut against the end surface of the second cylindrical portion 4 c and is fixed by a bolt B. The fixing method is not limited to this, and a method of fixing with a shaft nut is also used. The inner ring 12 b of the cylindrical roller bearing 12 is fixed so as to rotate integrally with the roller 4 sandwiched between the end surface of the first cylindrical portion 4 b and the annular member 15. In some cases, a gap is slightly provided between the end faces of the annular member 15 and the inner ring 12b in relation to the mounting accuracy of the housing.

  A donut plate-like lid member 16 is attached to the housing main body 11 using bolts B to fix the outer ring 12a. A seal 17 disposed in the central opening 16 a of the lid member 16 abuts on the annular member 15 and seals it. The housing body 11 and the lid member 16 constitute a housing. Although not shown, lubrication is often used by supplying grease, but an appropriate amount of lubricating oil containing lubricating oil is pumped into the housing from the oil / air lubrication device through the piping, and the cylindrical roller 12c. It is desirable to lubricate.

  FIG. 5 is a cross-sectional view of bearing devices 10 ′ and 10 ′ that support a roll having a large roll deflection such as a single roll 4 ′ for rolling the cast FE. In the present embodiment, the same bearing device 10 ′ and 10 ′ are used, but are used in an inverted manner, and therefore only one of them will be described. The bearing device 10 ′ differs from the above-described bearing device 10 only in the configuration of the cylindrical roller bearing 12 ′, and thus the description of the common configuration is omitted. However, the lid member 16 fixes the aligning ring 12 f to the housing body 11.

  FIG. 6 is an enlarged view of the cylindrical roller bearing 12 ′. In FIG. 6, the cylindrical roller bearing 12 ′ includes an aligning ring 12 f fitted to the inner circumference of the housing body 11, an outer ring 12 a fitted to the inner circumference of the aligning ring 12 f, and the second cylindrical portion 4 c of the roller 4. And an inner ring 12b fitted to the outer ring 12a and a plurality of cylindrical rollers 12c disposed between the outer ring 12a and the inner ring 12b. The outer periphery of the aligning ring 12f is a cylindrical surface, but its inner periphery is a spherical surface. On the other hand, although the raceway surface of the outer ring 12a is a cylindrical surface, the outer periphery thereof is a spherical surface corresponding to the inner peripheral surface of the aligning ring 12f. Therefore, the outer ring 12a is slidable and tiltable along the spherical surface with respect to the aligning ring 12f fitted and fixed to the housing body 11, thereby realizing the aligning function.

  Similar to the cylindrical roller bearing 12 described above, in the cylindrical roller bearing 12 ', the outer ring 12a is formed integrally with flanges 12d and 12d extending radially inward at both ends in the axial direction. The inner ring 12b is formed by integrally forming a flange 12e extending outward in the radial direction only at one end in the axial direction (here, the outer end with respect to the roller 4).

  The operation of this embodiment will be described. In the continuous casting facility shown in FIG. 1, the roller 4 rotates at an extremely low speed of about 2 to 3 rotations per minute in response to the supply of the cast FE. In the bearing devices 10 and 10 ′ provided in the roller unit 3, the cylindrical roller bearings 12 and 12 ′ rotatably support the rollers 4 and 4 ′ with respect to the housing body 11.

Here, since the total length of the roller 4 is shorter than the width of the slab FE, the amount of bending is small, and the inclination of the inner ring 12b of the cylindrical roller bearing 12 with respect to the housing body 11 is small even when supporting a large load. Therefore, there will be no problem due to edge loading. On the other hand, when a thrust load is applied from the slab FE to the roller 4, for example, to the left in FIG. 3, the flange portion 12e of the inner ring 12b of the right cylindrical roller bearing 12 is connected to the outer end of the cylindrical roller 12c. Since the thrust load is supported and the thrust load is supported, the movement of the roller 4 to the left can be restricted. In contrast, when a thrust load is applied from the slab FE to the roller 4 in the right direction in FIG. 3, for example, the flange portion 12e of the inner ring 12b of the left cylindrical roller bearing 12 is outside the cylindrical roller 12c. Since this thrust load is supported by abutting on the end portion, the movement of the roller 4 to the right can be restricted. Accordingly, the thrust loads in both directions applied to the roller 4 can be supported using the pair of cylindrical roller bearings 12. Thereby, in supporting the roller 4, the concept of the fixed side or the free side is eliminated, and the degree of freedom of layout of the roller 4 and the bearing device 12 is greatly expanded. Further, when the roller 4 is heated by the slab FE and thermal expansion occurs, the flange portions 12e of the inner rings 12b of the left and right cylindrical roller bearings 12 are displaced away from each other. Expansion can be escaped.

  On the other hand, since the total length of the roller 4 ′ is longer than the width of the cast piece FE, the amount of bending is relatively large. Since the outer ring 12a is inclined, problems such as edge loading do not occur. Also in the cylindrical roller bearing 12 ′, when a thrust load is applied from the cast FE to the roller 4 ′, for example, to the left in FIG. 5, the flange portion 12e of the inner ring 12b of the right cylindrical roller bearing 12 ′ is formed. Since the thrust load is supported by contacting the outer end of the cylindrical roller 12c, the leftward movement of the roller 4 'can be restricted. On the other hand, when a thrust load is applied to the roller 4 ′ from the cast FE to the right in FIG. 5, for example, the flange portion 12e of the inner ring 12b of the left cylindrical roller bearing 12 ′ becomes the cylindrical roller 12c. Since the thrust load is supported and the thrust load is supported, the movement of the roller 4 'to the right can be restricted. Therefore, the thrust load in both directions applied to the roller 4 ′ can be supported using the pair of cylindrical roller bearings 12 ′. Thereby, in supporting the roller 4 ′, the concept of the fixed side or the free side is eliminated, and the degree of freedom in layout of the roller 4 ′ and the bearing device 12 ′ is greatly expanded. Furthermore, when the roller 4 ′ is heated by the slab FE and thermal expansion occurs, the flange portions 12e of the inner rings 12b of the left and right cylindrical roller bearings 12 ′ are displaced in directions away from each other. The thermal expansion of 'can be escaped.

  FIG. 7 is a cross-sectional view similar to FIG. 3 showing a bearing device according to a modification of the present embodiment. FIG. 8 is a cross-sectional view similar to FIG. 5 showing a bearing device according to a modification of the present embodiment. In this modification, both cylindrical roller bearings 12 and 12 'are different in that the flange portion 12e of the inner ring 12b is disposed at an end portion near the center of the rollers 4 and 4' with respect to the cylindrical roller 12c. Even in this case, the thrust loads in both directions applied to the rollers 4 and 4 ′ can be similarly supported using the pair of cylindrical roller bearings 12 and 12 ′. However, in consideration of the case where the rollers 4 and 4 ′ are heated by the slab FE to cause thermal expansion, in the state of room temperature, the flange portion 12e of the inner ring 12b of the cylindrical roller bearings 12 and 12 ′, the cylindrical roller 12c, In between, take a structure that gives an appropriate amount of gap.

  The present invention has been described above with reference to the embodiments. However, the present invention should not be construed as being limited to the above-described embodiments, and can be changed or improved as appropriate. For example, the cylindrical roller bearing type may be a so-called full roller type or a bearing equipped with a cage. Further, the inner ring flange portions 12e and 12b of the cylindrical roller bearing are separate parts and a flange portion is provided at the end of 12b. Also good. Alternatively, a similar effect can be expected in a structure in which a flange is provided on both ends of the inner ring in the axial direction and a flange is provided only on one end of the outer ring.

It is a perspective view showing the outline of the continuous casting equipment using the bearing device concerning a 1st embodiment. It is a figure which shows the example of arrangement | positioning of the roll seen in the direction orthogonal to the moving direction of slab, and has shown the example of arrangement | positioning in one roll. It is a figure which shows the example of arrangement | positioning of the roll seen in the direction orthogonal to the moving direction of slab, and has shown the example of arrangement | positioning in two rolls. It is a figure which shows the example of arrangement | positioning of the roll seen in the direction orthogonal to the moving direction of slab, and has shown the example of arrangement | positioning in 3 rolls. It is sectional drawing of the bearing apparatuses 10 and 10 which support the one short roller 4 which rolls the slab FE. It is a figure which expands and shows the cylindrical roller bearing. It is sectional drawing of bearing apparatus 10 'and 10' which support one long roller 4 'which rolls cast FE. It is a figure which expands and shows the cylindrical roller bearing 12 '. It is sectional drawing similar to FIG. 3 which shows the bearing apparatus concerning the modification of this Embodiment. It is sectional drawing similar to FIG. 5 which shows the bearing apparatus concerning the modification of this Embodiment.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Introduction part 2 Discharge part 3 Roller unit 4, 4 'roller 4a Rolling part 4b 1st cylindrical part 4c 2nd cylindrical part 4d 3rd cylindrical part 10, 10' Bearing apparatus 11 Housing main body 11a Cylindrical part 11b Seal holding part 12, 12 'cylindrical roller bearing 12a outer ring 12b inner ring 12c roller 12d flange 12e flange 12f aligning ring 13 seal 14 labyrinth ring 15 annular member 16 lid member valve 17 seal FE slab

Claims (3)

A bearing device that is used in a continuous casting facility and rotatably supports the end of a roll with respect to a housing,
An outer ring that is supported by the housing and integrally formed on both ends in the axial direction with flanges extending radially inward;
An inner ring that supports the roll and has a flange that extends radially outward on one end side in the axial direction;
A bearing device, comprising: a plurality of cylindrical rollers disposed between the outer ring and the inner ring.   2. The roll bearing unit according to claim 1, wherein a flange portion of the inner ring is disposed on an outer side in the axial direction at both ends of the roll.   The outer peripheral surface of the outer ring is a spherical surface, and an aligning ring having an inner peripheral surface corresponding to the outer peripheral surface of the outer ring is disposed between the outer ring and the housing. Or the bearing unit of 2.

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