JP2009236278A - Bearing device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a bearing device used for supporting the fixed end of a roll in a continuous casting facility and suppressing abrasion and separation. <P>SOLUTION: A face-to-face duplex conical roller bearing allows the inclination of the roll to some extent. By exhibiting an original function to support an axial load, it is possible to support the fixed end of the roll. Thereby, in comparison with the use of a conical roller bearing with an aligning ring, load carrying capacity is increase. Also, in comparison with the use of a self-aligning roller bearing, abrasion and separation are effectively suppressed. <P>COPYRIGHT: (C)2010,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 Japanese Patent Laid-Open No. 10-220467

  Here, not only a severe load is applied to the bearing for the guide roll through the roll from the slab, but the surrounding environment is covered with water vapor because the cooling water is sprayed on the red slab. It is in a hot and humid environment. 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, there is provided 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, in the bearing device shown in Patent Document 2, the inner ring can be arbitrarily displaced in the axial direction, so that it cannot receive a thrust load and cannot be used on the fixed side of the roll. Therefore, even if the bearing device as shown in Patent Document 2 is used on the free side, a self-aligning roller bearing must be used on the fixed side, and the above-mentioned problem remains.

  SUMMARY OF THE INVENTION The present invention has been made in view of the above-described problems of the prior art, and it is an object of the present invention to provide a bearing device that can be used to support the fixed side end of a roll of a continuous casting facility, and that suppresses wear and peeling. .

  In a continuous casting facility, the bearing device of the present invention includes an outer ring attached to the housing, an inner ring attached to the roll, and an inner ring attached to the housing in order to rotatably support the fixed side end of the roll with respect to the housing. A front combination tapered roller bearing comprising a plurality of rollers disposed between an outer ring and the inner ring is used.

  For example, in a continuous casting machine, a roll unit composed of a plurality of rolls has been known for a long time. However, the roll is divided into two or more parts, arranged in the axial direction with respect to the slab, and cast. There are many split roll structures that improve the accuracy of single products. As a result of diligent research, the present inventors have found that since the roll length of these split rolls is short, the bending is suppressed to be smaller than that of a single roll, and a front combination tapered roller bearing can be applied to the fixed side. . This will be specifically described below.

  Referring to FIG. 1, points of action of the pair of rollers RL of the front combined tapered roller bearing (lines extending perpendicularly to the axis from the center of the roller) L1 and L2 intersect with the axis X of the front combined tapered roller bearing. When the distance Δ between the points P1 and P2 is less than about the width B / 2 of the front combined tapered roller bearing, the roll (not shown) supported by the front combined tapered roller bearing is inclined. Sometimes, compared with a cylindrical roller bearing, the support force against the moment of the roller RL is reduced, so that the deflection (tilt) of the roll can be allowed to some extent. The inventors of the present invention have found that bending can be allowed in the divided rolls in the above-described continuous casting machine, particularly by the design in which the positions of the action points P1 and P2 are suppressed within the range of B / 4.

  That is, it has been found that the tilt of the roll can be tolerated to some extent by the front combination tapered roller bearing, so the tapered roller bearing that supports the axial load, and the original function of the tapered roller bearing that supports the axial load, It can be supported and does not have a centering seat on the outer diameter surface of the bearing outer ring like a tapered roller bearing with a centering ring, so the load capacity can be increased, and a self-aligning roller bearing As compared with the case of using, wear and peeling can be effectively suppressed. The free end of the roll is preferably supported by a cylindrical roller bearing with a centering ring as shown in Patent Document 2, but may be supported by a self-aligning roller bearing.

  In the bearing device according to claim 2, when the roll is a split roll, bending of the roll is further suppressed, which is suitable for using a front combination tapered roller bearing. However, a front combination tapered roller bearing can be used to support a single roll as long as the deflection is acceptable. Here, “divided roll” refers to one roll when supported by a plurality of rolls along the width direction of the slab, and “single roll” refers to one roll along the width direction of the slab. It means the roll when it is supported by the roll.

  In the bearing device according to claim 3, it is preferable to form a crowning on the roller of the front combination tapered roller bearing because alignment can be further secured.

  In the bearing device according to claim 4, it is preferable to form crowning on at least one of the outer ring and the inner ring of the front combination tapered roller bearing because alignment can be further secured.

  6. The bearing device according to claim 5, wherein in the cross section of the front combined tapered roller bearing, when the width of the front combined tapered roller bearing is B, the action lines of the rollers on both sides in the axial direction are the same as the axis of the bearing. It is preferable that the distance Δ between two intersecting points is smaller than B / 4 because alignment can be further secured. Further, if the distance Δ between the two points is within B / 4, the action lines of the rollers on both sides in the axial direction may intersect with the axis of the bearing.

  7. The bearing device according to claim 6, wherein the bearing internal clearance dimension is such that a bearing internal clearance exists even when a temperature difference between the inner ring and the outer ring of the front combination tapered roller bearing is 10 ° C. Therefore, the roller is held between the inner ring and the outer ring by the heat at the time of roll rotation, and the roller is sandwiched over the circumference and a preload is applied in the radial direction, so that the operation of claim 5 is not disturbed. Is secured.

  In the bearing device according to claim 7, it is preferable that the front combination tapered roller bearing is a full-roller type because the load capacity can be further increased. However, a type having a cage may be used.

  Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings. FIG. 2 is a perspective view schematically showing a continuous casting facility using the bearing device according to the present embodiment. In the continuous casting equipment shown in FIG. 2, as shown in FIGS. 3A-5, a single roll (FIGS. 3A and 3B) having a bowl shape (a shape having a large diameter portion sandwiching a reduced diameter portion), A roll unit composed of a two-part roll (FIG. 4), a three-part roll (FIG. 5), or a plurality of more rolls than that is used. However, the arrangement and number of rolls arranged are various. Here, in the roll shown in FIG. 1, the arrangement of the rolls formed by a single piece having the hook shape shown in FIG. 6 is exemplarily shown.

  In FIG. 2, 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 | emission part 2 of 2 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.

  A roller unit 3A shown in FIG. 3A includes a single roller (also referred to as a guide roll) 4A for rolling the slab FE, a bearing device 10A that supports a fixed side end of the single roller 4A, and a single roller 4A. The bearing device 10B that supports the free side end portion and the two bearing devices 10C and 10D that support the intermediate portion 4f of the single roller 4A include about 5 to 8 rollers 4A in the flow direction of the cast piece. Arranged side by side. Several of them are connected to a driving device as driving rolls for extruding the cast FE. An example of the roll shape shown in the roller unit 3A is as shown in FIG. 3B, but the length of the rolling portion 4a is changed to a long, medium, short by changing the position supported by the bearing devices 10C and 10D. Therefore, the description is omitted here.

  FIG. 6 is a view in which the roll shape represented in the configuration of FIG. 3A is cut along the VI-VI line and viewed in the direction of the arrow. In FIG. 6, the single roller 4A has three rolling portions 4a for rolling the slab FE, and these are coaxially connected to each other by a small diameter portion 4e. On the left side of the left rolling part 4a in FIG. 6, the first cylindrical part 4b, the second cylindrical part 4c, and the third cylindrical part 4d, which are smaller in diameter than the rolling part 4a and are arranged coaxially, The first cylindrical portion 4b, the second cylindrical portion 4c, the second cylindrical portion 4c, and the first cylindrical portion 4c are arranged on the right side of the rolling portion 4a. Three cylindrical portions 4d are provided in this order from the rolling portion 4a side. Needless to say, it is not always necessary to provide the cylindrical portions 4b, 4c, and 4d, and the shape of the end of the roller 4A can be changed according to the specifications.

  In FIG. 6, 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. 7 is an enlarged view of the front combination tapered roller bearing 12 that supports the fixed side end of the single roller 4A. In FIG. 4, the front combination tapered roller bearing 12 includes a pair of outer rings 12a and 12a fitted to the inner periphery of the housing body 11, an inner ring 12b fitted loosely to the second cylindrical portion 4c of the roller 4A, and an outer ring. It consists of a plurality of cylindrical rollers 12c, 12c arranged in a double row between 12a, 12a and the inner ring 12b, and cages 12d, 12d for holding the cylindrical rollers 12c, 12c. The outer rings 12a and 12a each have a tapered raceway surface whose diameter increases toward the inside, and the inner ring 12b has a pair of tapered raceway surfaces whose diameter increases toward the inside. The action lines (see FIG. 1) of the rollers 12c and 12c that roll along the raceway surface substantially intersect with each other on the axis of the front combination tapered roller bearing 12.

  It is preferable to form crowning at both ends of the roller 12c so that the diameter of the roller 12c is reduced by a slight amount toward the end, since the edge load is alleviated. If the length of the roller 12c is larger than the roller diameter, it is preferable because the roller can be prevented from falling. Further, if the outer ring 12a and the inner ring 12b are also formed with a crowning that expands by a small amount toward the end of the roller 12c, the edge load may occur when the roll is bent due to the bending of the roll. Since it is relieved, it is more preferable.

  In FIG. 7, the outer rings 12a and 12a have a structure in which the outer rings 12a are abutted with each other, and there is no spacer at the center, so that the clearance inside the bearing is adjusted. Further, a plurality of oil grooves 12h, 12h extending in the radial direction are formed on the circumference of the abutting end faces of the outer rings 12a, 12a so that the lubricating oil can be supplied from the housing side. Since this structure does not have a spacer (described later with reference to FIG. 9) for adjusting the clearance at the center, there is an advantage that it can be used without being restricted by the width dimension of the oil groove on the housing side. That is, since the spacer is not provided even if the oil groove width on the housing side is wide, there is no concern that the spacer will fall into the oil groove.

  Further, at the end in the axial direction of the inner ring 12b, a plurality of oil grooves 12g extending in the radial direction are formed on the end face with which an annular member 15 described later contacts, and even if the annular member 15 contacts, Further, the lubricating oil can be supplied to the inner diameter side of the inner ring 12b, and the lubricant (oil / grease) can flow into the fitting surface of the inner diameter surface of the roller 4A and the inner ring 12b. As a result, insufficient lubrication of the fitting surface is alleviated, and it is also possible to prevent damage such as wear and galling caused by creep generated on the fitting surfaces of the inner diameter surfaces of the roller 4A and the inner ring 12b. In addition, a spiral groove may be provided on the inner diameter surface of the inner ring 12b to further retain the lubricant from the end face side, thereby improving the long-term durability of the fitting surface. Further, as indicated by a dotted line, an oil groove penetrating in the radial direction can be provided in the center of the inner ring 12b. Furthermore, it is more preferable that a lubricating coating is formed on the inner peripheral surface of the inner ring 12b. Examples of the lubricating coating include a manganese phosphate coating, a tin-zinc alloy coating, and a black dye coating.

  In FIG. 6, an annular member 15 is fitted and disposed on the outer periphery of the third cylindrical portion 4 d of the left 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. . However, the fixing method is not limited to this, and a fixing method using a shaft nut is also used. The inner ring 12b of the front combination tapered roller bearing 12 may be pressed and fixed so as to rotate integrally with the roller 4A held between the end surface of the first cylindrical portion 4b and the annular member 15. In general, the inner diameter surface of the inner ring 12b and the roller 4A are loosely fitted, and therefore, slippage may occur between the annular member 15 due to creep and the end surface of the inner ring 12b, causing slight wear. The end surface of the inner ring 12b is set with a clearance. Since these set states vary depending on the structure of the roller 4A, the oil groove 12g is provided on the end surface of the inner ring 12b regardless of the set state of the annular member 15 and the inner ring 12b by the oil groove on the end surface of the inner ring 12b. Is desirable.

  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. However, an appropriate amount of lubricating oil containing lubricating oil is pumped into the housing from the oil / air lubricating device via piping, and the rollers 12c, 12c may be lubricated.

  FIG. 8 is an enlarged view of the cylindrical roller bearing 112 provided with the aligning ring 112f that supports the free side end portion of the single roller 4A. In FIG. 8, the cylindrical roller bearing 112 is disposed between the outer ring 112a fitted to the inner periphery of the housing body 11, the inner ring 112b fitted to the second cylindrical portion 4c of the roller 4A, and the outer ring 112a and the inner ring 112b. A plurality of cylindrical rollers 112c. The outer ring 112a is formed by integrally forming flanges 112d and 112d extending radially inward at both ends in the axial direction so as to sandwich the cylindrical roller 112c.

  In FIG. 6, an annular member 15 is fitted and disposed on the outer periphery of the third cylindrical portion 4 d of the right 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. . However, the fixing method is not limited to this, and a fixing method using a shaft nut is also used. The inner ring 112b of the cylindrical roller bearing 112 is fixed so as to be integrally rotated with respect to the roller 4A sandwiched between the end surface of the first cylindrical portion 4b and the annular member 15.

  In some cases, a clearance may be provided between the end faces of the annular member 15 and the inner ring 112b slightly due to the mounting accuracy of the housing. The inner ring 112b may be pressed and fixed so as to rotate integrally with the roller 4A held between the end surface of the first cylindrical portion 4b and the annular member 15, but in general, the inner ring 112b is fixed. Since the inner diameter surface and the shaft of the inner ring 112 are loosely fit, slipping may occur between the annular member 15 due to creep and the end surface of the inner ring 112b, causing slight wear. Set to give. Since these set states vary depending on the structure of the roll, the inner ring 112b is not influenced by the set state of the annular member 15 and the inner ring 112b by the oil groove on the end surface of the inner ring 112b, and is similar to the tapered roller bearing 12 on the fixed side. It is desirable to provide an oil groove in the radial direction on the end face of this.

  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 in the figure, lubrication is often used by supplying grease, but an appropriate amount of lubricating oil including lubricating oil is pumped into the housing via a pipe from an oil / air lubricating device, and the cylindrical roller 12c. May be lubricated.

  The cylindrical roller bearings 12C of the bearing devices 10C and 10D that support the intermediate portion 4f of the single roller 4A with respect to the housing need only be supported so as to be capable of relative displacement of the single roller 4A. Details are not described here.

  FIG. 9 is an enlarged view showing a modified example of the front combination tapered roller bearing 12 ′ that supports the fixed side end portion of the single roller 4 </ b> A. The modification shown in FIG. 9 differs from the embodiment of FIG. 7 in that a spacer 12f is formed between the pair of outer rings 12a and 12a.

  FIG. 10 is an enlarged view showing another modified example of the front combination tapered roller bearing 12 ″ supporting the fixed side end of the single roller 4A. In the modified example shown in FIG. However, the inner ring 12b is divided into two parts in the axial direction, and damage such as wear and galling caused by creep generated on the fitting surfaces of the inner diameter surfaces of the roller 4A and the inner ring 12b is prevented. Therefore, a plurality of oil grooves (illustrated by dotted lines) extending in the radial direction on the butt end face can be formed on the circumference so that oil can be easily introduced into the inner diameter surface of the inner ring 12b from the two split surfaces of the inner ring 12b.

  FIG. 11 is an enlarged view showing a modified example of the front combination tapered roller bearing 12 ″ ′ that supports the fixed side end of the single roller 4A. In the modified example shown in FIG. In contrast to the configuration, a spacer 12f is formed between the pair of outer rings 12a and 12a, and the inner ring 12b is divided into two in the axial direction. A plurality of oil grooves (illustrated by dotted lines) extending in the radial direction on the abutting end surface can be formed on the circumference so that oil can be easily introduced into the inner diameter surface of the inner ring 12b from the two split surfaces.

Next, in the roller unit 3B shown in FIG. 4, the split rolls 4B and 4C which are shorter than the width of the slab and configured by two pieces are used. As shown in FIG. 4, it is desirable that the split rolls 4B having a long overall length and the split rolls 4C having a short overall length are alternately arranged in the flow direction of the slab. Here, there are four support ends of the split rolls 4B and 4C arranged coaxially.
(4B left end-4B right end, 4C left end-4C right end) =
(Free end-Fixed end, Fixed end-Free end),
(Free end-Fixed end, Free end-Fixed end),
(Fixed end-free end, fixed end-free end),
There are four types (fixed end-free end, free end-fixed end), but the bearing device according to the present invention may be arranged at the fixed end of any roll arrangement.

  FIG. 12 is a view of a roll shape (in this case, the divided roller 4B) typified by the configuration of FIG. 4 taken along line XII-XII and viewed in the direction of the arrow. In FIG. 12, the division | segmentation roller 4B has the rolling part 4a which rolls the slab FE. On both sides of the rolling part 4a, a first cylindrical part 4b, a second cylindrical part 4c, and a third cylindrical part 4d, which are smaller in diameter than the rolling part 4a and arranged coaxially, are arranged in this order on the rolling part 4a side. It is provided from. Needless to say, it is not always necessary to provide the cylindrical portions 4b, 4c, and 4d, and the shape of the end of the roller 4B can be changed according to the specifications.

  In FIG. 12, a cylindrical portion 11a and a seal holding portion 11b are coaxially formed inside the housing body 11 with the lower surface 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. In FIG. 12, a front combined tapered roller bearing 12 is attached to the left housing body 11, and a cylindrical roller bearing 112 is attached to the right housing body 11, which are the same as those shown in FIGS. Therefore, explanation is omitted.

  In FIG. 12, an annular member 15 is fitted and disposed on the outer periphery of the third cylindrical portion 4 d of the left 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. . However, the fixing method is not limited to this, and a fixing method using a shaft nut is also used. The inner ring 12b of the front combination tapered roller bearing 12 may be pressed and fixed so as to rotate integrally with the roller 4B sandwiched between the end surface of the first cylindrical portion 4b and the annular member 15. In general, the inner diameter surface of the inner ring 12b and the roller 4B are loosely fitted, and therefore, slippage may occur between the annular member 15 due to creep and the end surface of the inner ring 12b, causing slight wear. The end surface of the inner ring 12b is set with a clearance. Since these set states vary depending on the structure of the roller 4B, the oil groove 12g is provided on the end surface of the inner ring 12b regardless of the set state of the annular member 15 and the inner ring 12b by the oil groove on the end surface of the inner ring 12b. Is desirable.

  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. However, an appropriate amount of lubricating oil containing lubricating oil is pumped into the housing from the oil / air lubricating device via piping, and the rollers 12c, 12c may be lubricated.

Next, in the roller unit 3 </ b> C shown in FIG. 5, split rollers 4 </ b> D, 4 </ b> E, and 4 </ b> F each having a total length shorter than the width of the slab are used. It is desirable that the split roll 4D having the longest length, the split roll 4E having the intermediate length, and the roll 4F having the shortest full length are alternately arranged in this order and in the reverse order in the flow direction of the slab. (See FIG. 5). Here, there are six supporting ends of the split rolls 4D, 4E, and 4F arranged in the same axis.
(4D left end-4D right end, 4E left end-4E right end, 4F left end-4F right end) = (free end-fixed end, fixed end-free end, fixed end-free end),
(Fixed end-free end, free end-fixed end, free end-fixed end),
(Free end-Fixed end, Fixed end-Free end, Free end-Fixed end),
Although there are four types (fixed end-free end, fixed end-free end, fixed end-free end), the bearing device according to the present invention may be arranged at the fixed end of any roll arrangement.

  A front combination tapered roller bearing 12 is attached to one housing body 11 supporting the divided rolls 4D, 4E, and 4F, and a cylindrical roller bearing 112 is attached to the other housing body 11, which are shown in FIGS. Since it is the same as that shown in FIG.

  The operation of this embodiment will be described. In the continuous casting facility shown in FIG. 2, the rollers 4 </ b> A to 4 </ b> F rotate at an extremely low speed of about 1 to 5 rotations per minute according to the supply of the cast FE. In the bearing device 10 provided in the roller units 3A to 3C, the front combination tapered roller bearing 12 and the cylindrical roller bearing 12 support the rollers 4A to 4F rotatably with respect to the housing body 11.

  In particular, since the total length of the divided rollers 4B to 4F is shorter than the width of the cast FE, the amount of bending is small, and it is suitable for supporting the fixed side end portion by the front combination tapered roller bearing 12. On the other hand, when a thrust load is applied from the slab FE to the roller 4, for example, the front combination tapered roller bearing 12 supports the thrust load, so that the axial displacement of the rollers 4A to 4F can be limited. Further, when the rollers 4A to 4F are heated by the slab FE to cause thermal expansion, the flange portion 12e of the inner ring 12b of one cylindrical roller bearing 12 is displaced in a direction away from each other, and thus the roller 4A. Thermal expansion of ~ 4F can be released.

  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, as the front combined tapered roller bearing type, either a so-called full roller type or a bearing provided with a cage may be used. The free end of the roller may be supported by a self-aligning roller bearing.

It is a figure for demonstrating the action line of a front combination tapered roller bearing. It is a perspective view which shows the outline of the continuous casting installation using the bearing apparatus concerning this 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 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 division | segmentation 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 three division | segmentation rolls. It is the figure which cut | disconnected the structure of FIG. 3A by the VI-VI line and looked at the arrow direction. It is a figure which expands and shows the front combination tapered roller bearing. It is a figure which expands and shows the cylindrical roller bearing 112. It is a figure which expands and shows the front combination tapered roller bearing concerning a modification. It is a figure which expands and shows the front combination tapered roller bearing concerning a modification. It is a figure which expands and shows the front combination tapered roller bearing concerning a modification. It is the figure which cut | disconnected the structure of FIG. 4 by the XII-XII line | wire, and looked at the arrow direction.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Introduction part 2 Discharge part 3A-3C Roller unit 4A-4F Roller 4a Rolling part 4b 1st cylindrical part 4c 2nd cylindrical part 4d 3rd cylindrical part 10A, 10B, 10C Bearing apparatus 11 Housing main body 11a Cylindrical part 11b Seal holding part 12 front combination tapered roller bearing 12a outer ring 12b inner ring 12c roller 12d cage 12e spacer 112 cylindrical roller bearing 112a outer ring 112b inner ring 112c roller 112d flange 112e flange 112f alignment ring 13 seal 14 labyrinth ring 15 annular member 16 lid member valve 17 Sealed FE slab

Claims (7)

  In a continuous casting facility, between the outer ring attached to the housing, the inner ring attached to the roll, and the outer ring and the inner ring to rotatably support the fixed end of the roll with respect to the housing. A bearing device using a front combination tapered roller bearing comprising a plurality of rollers disposed on the surface.   The bearing device according to claim 1, wherein the roll is a split roll.   The bearing device according to claim 1, wherein a crowning is formed on a roller of the front combination tapered roller bearing.   The bearing device according to claim 1, wherein a crowning is formed on at least one of the outer ring and the inner ring of the front combination tapered roller bearing. In the cross section of the front combined tapered roller bearing, when the width of the front combined tapered roller bearing is B, the distance Δ between the two points where the action lines of the rollers on both sides in the axial direction intersect with the axis of the bearing is B It is smaller than / 4, The bearing apparatus in any one of Claims 1-4 characterized by the above-mentioned.   The bearing internal clearance is such that a gap remains in the bearing even when the temperature difference between the inner ring and the outer ring of the front combination tapered roller bearing becomes 10 ° C. The bearing device according to any one of 5.   The bearing device according to claim 1, wherein the front combination tapered roller bearing is a full roller type.

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