JPS63183709A - Bearing device for roll of rolling mill - Google Patents

Abstract

PURPOSE:To remarkably improve the bearing rated load and to save labor in maintenance and checking work by employing a grease filling type for double row cylindrical roller bearings and installing both end faces of a cylindrical roller to be approximately flush with both end faces of a chock. CONSTITUTION:Double row cylindrical roller bearings 11, 12 are fitted on a large dia. shaft part 3b and a medium dia. shaft part 3c. Oil seals 15c, 16c are put between guide rings 15, 16 installed on both end face parts of outer rings 11b, 12b of the bearings 11, 12 and the extended part of inner rings 11a, 12a to form the bearings 11, 12 into a grease filling type. The inner rings 11a, 12a are designed so that both end faces of cylindrical rollers 11c, 12c are approximately flush with both end faces A, B of a chock 4. As the result, the rated load of the bearings 11, 12 is remarkably improved and the bearings 11, 12 are made to be maintenance free and save labor in maintenance and checking work because of the grease filling type.

Description

DETAILED DESCRIPTION OF THE INVENTION [Industrial Application Field] The present invention relates to a bearing device suitable for rolling mill rolls, particularly for backup rolls.

[Prior art]

Generally, a four-high rolling mill with backup rolls arranged above and below the work roll is widely used as a rolling mill for various plate materials. , both ends of the backup roll are supported by the chocks of the upper and lower stands, respectively, the work roll protruding from the chocks, and the shaft portion at one end of the backup roll are connected to a drive motor, respectively, and are driven to rotate by the drive of the motors. It is now possible to

Conventionally, sliding bearings using oil film, tapered roller bearings, cylindrical roller bearings, etc. have been used as bearing devices for rolling rolls for such chocks, and the lubrication methods include oil circulation type, grease filled type, oil mist type, etc. as appropriate. They are used in combination.

FIG. 2 is a partial sectional view of a sliding bearing using an oil film, which is generally used as a bearing for bank-up rolls in a rolling mill. A sleeve 5 whose diameter gradually decreases from the root toward the shaft end to have a tapered outer circumferential surface and a tapered inner circumferential surface around the outer circumferential surface.
2a and apply a key 52b, and the sleeve 52a
A shell 54a made of a bearing material such as white metal is interposed between the chock 54 and the chock 54, and an oil film is formed between the shell 54a and the sleeve 52a.

However, in such oil film type sliding bearings, it is often difficult to form an oil film during low speed rolling in a high load range, and seizure is likely to occur.Also, even if seizure does not occur, the oil film thickness changes during low speed rolling. However, there were drawbacks such as being one of the causes of changes in the exit side plate thickness.

For this reason, recently, bearing devices using cylindrical roller bearings have been adopted as bearings for rolling rolls, and the applicant of this application has already filed an application.
No. 44116).

FIG. 3 is a partial cross-sectional view of the bearing device for a backup roll according to this application, in which the roll neck 3 of the backup roll I is gradually reduced in diameter from the barrel 2 side toward the shaft end side so that it has a substantially truncated conical shape. The eggplant has five parts: a root part 3a, a cylindrical large diameter shaft part 3b, a medium diameter shaft part 3c, a small diameter shaft part 3d, and a shaft end part 3e. The portions 3c are rotatable directly or indirectly to the chock 4 by using oil circulating type double row cylindrical roller bearings 31 and 32, and the small diameter shaft portion 3d is using a grease filled type double row tapered roller bearing 33. It is a must to support.

The large-diameter shaft portion 3b and the medium-diameter shaft portion 3c in the roll neck 3 have approximately the same longitudinal dimension, and the sum of the longitudinal dimensions of both wheels is the width dimension between both sides A and B of the chock 1 in the same direction. The boundary between the large-diameter shaft portion 3b and the root portion 3a on the barrel 2 side, and the boundary between the medium-diameter shaft portion 3c and the small-diameter shaft portion 3d are set equal to both sides A of the chock 4, respectively. It is set to be located approximately in the same vertical plane as B or in the vicinity thereof.

Each double row cylindrical roller bearing 31, 32 has its inner ring 31a, 32
a and outer rings 31b and 32b, which are provided with inner flanges 31e and 32e at the central part of the inner peripheral surface in the axial direction, respectively, the inner flanges 31e.
, 32e, and accommodates two rows of cylindrical rollers 31c, 32c, each supported by retainers 31d, 32d, and is configured to form a four-row cylindrical roller bearing as a whole.

The inner and outer diameters of the inner rings 31a and 32a are set to be equal to each other, and the longitudinal dimensions of the inner rings 31a and 32a are set to be equal to those of the large-diameter shaft portion 3b and the medium-diameter shaft portion 3c, respectively. 3b directly, and the inner ring 32a is tightly fitted to the medium diameter shaft portion 3c indirectly with a cylindrical ring 34 interposed therebetween.

The inner rings 31a and 32a have opposite end portions abutted against each other near the boundary between the large diameter shaft portion 3b and the medium diameter shaft portion 3c, and the barrel side end of the inner ring 31a is attached to the root portion 3.
A thrust collar 37, which is keyed to the small diameter shaft portion 3d, butts against the fillet ring 36 fitted onto the outside of the inner ring 32a, and a thrust collar 37 keyed to the small diameter shaft portion 3d abuts against the shaft end side end of the inner ring 32a to prevent removal.

On the other hand, the outer rings 31b and 32b have opposing ends abutted against each other with a spacer ring 35 interposed between them, and the barrel side end of the outer ring 31b is connected to the guide ring 31.
The rear cover 38 is screwed onto the protruding portion 4b from the chock 4 with the interposition of the guide ring 32g and the retaining ring 39 interposed between the end face of the outer ring 32b on the shaft end side. It abuts against the front cover 40 which is screwed onto the overhanging portion 4c, and is similarly prevented from being removed.

Inner flanges 31e and 32e of outer rings 31b and 32b, outer peripheral surfaces of outer rings 31b and 32b facing these, and chocks 4
Lubricating oil supply passages 31F and 32f are provided on the circumferential surface of the hole 4a, and a lubricating oil discharge passage 35a is provided on the spacer ring 35 interposed between the outer rings 31b and 32b and on the circumferential surface of the hole 4a facing the spacer ring 35. The lubricating oil supplied from both supply passages 31f and 32f circulates within each bearing 31 and 32, and then is discharged from the discharge passage 35a.

Note that the space between the fillet ring 36 and the rear lid 38 is sealed with oil seals 38a, 38b, 38c, etc., and the space between the stop ring 39 and the thrust collar 37 is also sealed with a similar oil seal 391, etc.

The double-row tapered roller bearing 33 includes an inner ring 33a and an outer ring 33b,
Tapered rollers 33c and 33C are connected between cage 33d and 33b.
The inner ring 33a is tightly fitted into the small diameter shaft portion 3d of the roll neck 3 with the end on the barrel side abutting the thrust collar 37, and the end on the shaft end side A lock nut 42 screwed onto the shaft end 3e is abutted against the shaft end 3e to prevent the shaft from being pulled out. On the other hand, outer ring 33b13
3b is a thrust housing 4 fixed to the front cover 38;
0a, it is held captive by a thrust cover 40b, and grease is sealed inside.

[Problem that the invention seeks to solve]

However, since such conventional double-row cylindrical roller bearings use a method to circulate lubricating oil, it is necessary to provide a circulation system such as an oil supply path and an oil discharge path, making the configuration complicated and causing problems such as oil leakage. It is difficult to avoid contaminating the surrounding area due to such problems, and furthermore, when replacing the rolls, the work of shutting off and connecting the supply path and discharge path becomes complicated. Moreover, in the conventional method, as is clear from FIG.
The dimensions between B are approximately equal, and the double row cylindrical roller bearing 31.3
Since the axial dimensions of the inner rings 31a and 32a of No. 2 are set approximately equal to the axial dimensions of the large-diameter shaft portion 3b and medium-diameter shaft portion 3c of the roll neck 3, respectively, the shaft of the cylindrical rollers 31c and 32c Cylindrical rollers 31c and 32c located at both ends in the longitudinal direction
The end faces of the chock 4 are 11°1 from the sides A and B of the chock 4, respectively.
2 was placed inward, and there was a structural limit to increasing the rated load, and the structure itself was also wasteful.

The present invention has been made in view of the above circumstances, and its purpose is to provide a lubricating method without making major modifications to a bearing device using a conventional double-row cylindrical roller bearing and its surrounding structure. A grease sealing system is adopted, and the rated load is also increased.

The object of the present invention is to provide a bearing device equipped with a double-row cylindrical roller bearing.

[Means for solving problems]

In the present invention, the double-row cylindrical roller bearing, which supports the shaft portions of roll necks formed with different diameters on chocks, has the ends of the inner ring located on both ends of the shaft in the axial direction closer to the chock end face in the axial direction. Also, the end faces of the cylindrical rollers in the same direction are positioned as close to the chock end face as possible within the same plane as this, and the cylindrical rollers arranged on both ends of the outer ring in the axial direction are An oil seal for sealing grease is provided between the guide ring and the extension of the inner ring.

[Effect]

According to the present invention, the grease-sealed structure is maintenance-free, and the support area of the cylindrical rollers and chocks relative to the roll neck is increased, resulting in a larger rated load.

〔Example〕

DESCRIPTION OF THE PREFERRED EMBODIMENTS The present invention will be specifically described below based on drawings showing embodiments thereof. FIG. 1 is a partial cross-sectional view showing how the apparatus of the present invention is used. In the figure, 1 indicates a backup roll of a rolling mill, 2 indicates a barrel, 3 similarly indicates the roll neck, and 4 indicates a chock. The roll neck 3 is gradually reduced in diameter from the barrel 2 side toward the shaft end side to form a substantially truncated conical shape, and the base 3a, which is connected to the top side and forms a short cylindrical part, has a cylindrical shape. A large diameter shaft portion 3b, a medium diameter shaft portion 3c, and a small diameter shaft portion 3d forming a
and a shaft end portion 3e are formed in this order from the barrel 2 side to the shaft end side, and the large diameter shaft portion 3b and the medium diameter shaft portion 3c are formed by grease-sealed double row cylindrical roller bearings 11 and 12, respectively. It is directly supported by the chock 4, and the small diameter shaft portion 3d is also indirectly supported by the chock 4 via the front lI 21 by a grease-sealed double-row tapered roller bearing 13.

The roll neck 3 has a large diameter shaft portion 3b having a dimension slightly larger than 2, which is the width between both end surfaces A and B of the chock 4 in the axial direction, and a medium diameter shaft portion 3c having a dimension in the axial direction. A, B
The chock is set to approximately % of the width dimension between A and B of the chock 4, and the boundary between the large diameter shaft portion 3b and the medium diameter shaft portion 3c is aligned with approximately the center of the width dimension between A and B of the chock 4. It is supported by 4.

In this state, the boundary between the roll neck 3 and the root 3a is located closer to the barrel 2 than the side A of the chock 4, and the boundary between the medium diameter shaft 3c and the small diameter shaft 3d is located on the side of the chock 4. It is located approximately on the same vertical plane as B.

Both double row cylindrical roller bearings 11 and 12 have their inner rings 11a.
.

12a and inner flange 11e, 12e at the center of the axial direction of the inner peripheral surface.
The inner flange 11e is provided between the outer rings 11b and 12b provided with the
Two rows of cylindrical rollers each divided by 12e, 12c
It is configured as a two-row cylindrical roller bearing in which the bearings are accommodated using cages 11d and 12d, respectively.

Each inner ring 11a, 12a of each double row cylindrical roller bearing 11.12
The inner diameter of the inner ring 12a is approximately equal to the diameter of the large-diameter shaft portion 3b and the medium-diameter shaft portion 3c of the roll neck 3, and the outer diameters, which are raceway diameters, are set to be equal to each other. The inner ring 11a is thicker than the inner ring 11a by an amount corresponding to the difference in diameter between the inner ring 3b and the medium diameter shaft part 3c, and the inner ring 11a is thicker than the inner ring 11a.
In addition, the inner rings 12a are tightly fitted to the medium-diameter shaft portion 3c, and when mounted on the roll neck 3, the double-row cylindrical roller bearings 11 and 12 constitute a four-row cylindrical roller bearing as a whole. It has become.

Further, the axial dimension of the inner ring 11a is approximately equal to that of the large diameter shaft portion 3b, and the axial dimension of the inner ring 12a is set slightly longer than that of the medium diameter shaft portion 3c.
, 12a are abutted against each other at the boundary between the large-diameter shaft portion 3b and the medium-diameter shaft portion 3c, and the end face of the inner ring 11a on the barrel 2 side is fitted externally into the root portion 3a. The end face of the inner ring 12a on the shaft end side extends from the boundary between the medium diameter shaft portion 3c and the small diameter shaft portion 3d onto the small diameter shaft portion 3c as an overhanging soft tube; The end face of a thrust collar 19 which is keyed to the small diameter shaft portion 3c is abutted against the end face to prevent removal.

In addition, each outer ring 11b of the double-row cylindrical roller bearing 11.12, 1
2b has the same inner and outer diameters, and the dimension in the axial direction is set slightly smaller than the approximate dimension between end surfaces A and B of the chock 4, and the center part of the inner peripheral surface in the axial direction is entirely The inner ring 11a is provided with an inner ring 12e over the circumference, and a spacer ring 14 is interposed between the inner rings 11a and 12e.
, 12a, and the end surface of the outer ring 11b on the barrel 2 side is located slightly inside the end surface A of the chock 4 on the barrel 2 side, and a guide ring 15 is inserted between the end surface of the outer ring 11b and the end surface A of the chock 4 on the barrel 2 side. The overhanging part 4b of the chock 4
The shaft end side end face of the outer ring 12b is positioned on the same vertical plane as the end face B of the chock 4, respectively, and a guide ring 16 and a retaining ring 20 are provided on the end face.
The front cover 21, which is also provided on the protruding portion 4c of the chock 4, is pressed against the chock 4 to prevent it from being removed. In this state, the barrel 2 side end surface of the guide ring 15 is the barrel 2 side of the inner ring 11a.
The side end face and the end face on the shaft end side of the guide ring 16 are connected to the inner ring 1.
It is located substantially on the same plane as the shaft end side end surface of 2a.

Note that the outer rings 11b and 12b of a conventional oil circulating type cylindrical roller bearing 31, 32 as shown in FIG.
.

When reusing 32b, it is a lubricating oil supply path 31f.

Plugs 11h, 12h, and 14h may be tightly fitted into the discharge passage 32f and the discharge passage 35a to seal them.

The cylindrical rollers llc+12c are the inner rings 11a, 12
a and the outer rings 11b and 12b, and the outer ring 11b
, inner flange 11e, 12e of 12b, spacer ring 14
The bearings are separated from each other by guide rings 15 and 16 and held in cages 11d and 12d, respectively, so as to constitute a four-row cylindrical roller bearing as a whole.

Among the cylindrical rollers 12c, the end surfaces of the cylindrical rollers located at both ends are the end surfaces A on the barrel 2 side of the chock 4, respectively.
The lengths and positions of the cylindrical rollers Ilc and 12c are set so that they are located on a plane substantially perpendicular to the end surface B on the shaft end side.

The outer diameter of each guide ring 15, 16 is equal to the diameter of the hole 4a of the chock 4, and the inner diameter is set slightly smaller than the inner diameter of the outer rings 11b, 12b.
Flange edges 15a and 15b are provided on the peripheral edge of the end surface on the b side and on the barrel 2 side of the inner peripheral surface, respectively, and flanges 15a and 15b are provided on the peripheral edge of the end surface of the guide ring 16 on the outer ring 12b side and on the shaft end side of the inner peripheral surface, respectively. It is provided with collar edges 16a and 16b, each collar edge 15a.

16a is fitted into a notch edge formed in the outer rings 11b, 12b and abuts against the outer rings 11b, 12b.

The inner peripheral surface side of this guide ring 15, 16 and the flange edge 15
Inner rings 11a and 12 are provided with lips on the inside of rings b and 16b, respectively.
The oil seal 1 is in sliding contact with the outer circumferential surface of the extended portion of a.
5c, 16c are arranged, and inner and outer rings 11a, 12a,
12b, 12b, and the guide ring 15.16
This is to seal the grease filled in between.

Grease as a lubricant is filled during assembly or overhaul, but since the double row cylindrical roller bearing 11.12 is sealed with oil seals 15c, 16c, etc., stable lubrication is ensured. On the other hand, it is predicted that the bearing temperature will increase as a result of the increase in the heat of stirring of the grease in the bearing and the decrease in the heat dissipation effect, so the cylindrical roller 11c,
The mutual gap between 12c is made slightly larger, and the amount of grease sealed is also less than the standard, in order to reduce the heat of stirring.

Further, the binding force of the lips of the oil seals 15c, 16c is set to be much smaller than the standard value, since there is a possibility that the inner rings 11a, 12a may cause an abnormal temperature rise due to the frictional heat of the sliding pressure.

The rear 118 is a bolt 1 attached to the protrusion 4b from the chock 4.
8g, and a plurality of oil seals 18a2... are provided between the fillet ring 17 and the extending portion facing the fillet ring 17.

On the other hand, the front M21 is the same (the protruding portion 4c from the chock 4).
The small-diameter shaft portion 3d of the roll neck 3 is fastened to the small diameter shaft portion 3d of the roll neck 3 by interposing the thrust cover 21b arranged on the side surface of the shaft end of the thrust housing 2181 arranged on the inner periphery of the thrust housing 2181.
is supported by a double-row tapered roller bearing 13.

This double row tapered roller bearing 13 includes an inner ring 13a and an outer ring 13b.
It is configured as a two-row tapered roller bearing in which tapered rollers 13c, 13c are housed between the bearing 13b and the roller 13b. The inner ring 13a has its end face on the barrel 2 side abutted against the thrust collar 19, and its end face on the shaft end side abuts against a lock nut 22 screwed onto the shaft end 3e to prevent the inner ring 13a from being pulled out.

On the other hand, the outer rings 13b and 13b have a spacer 13e between them.
are interposed, and retaining rings 13f, 13f are provided at both ends.
113g fitted inside the retaining rings 13f, 13f (7).
, 13g of grease filled inside is sealed.

In the device of the present invention as described above, among the double row cylindrical roller bearings 11 and 12 that support the large diameter shaft portion 3b and the medium diameter shaft portion 3c of the roll neck 3, the cylindrical roller bearing that supports the medium diameter shaft portion 3c is used. The inner ring 12a of the cylindrical roller bearing 12 has a larger wall thickness, and its outer diameter is set equal to the outer diameter of the inner ring 11a of the cylindrical roller bearing 11.
4 (see Figure 3), the number of parts is reduced accordingly, and the outer ring 11 of both double row cylindrical roller bearings 11 and 12 is not required.
b, 12b and cylindrical rollers located at both ends, 12
Both the barrel side end face and the shaft end face of c are chock 4.
Since it is located on the same vertical plane as both end faces A and B, or as close to it as possible within a range that does not exceed this, the permissible load value is large, there is no structural waste, and furthermore, both ends are Guide rings 15.16 and inner rings 11a, 12a provided at both ends of the outer rings 11b, 12b of the row cylindrical roller bearings 11.12.
Since oil seals 15c and 16c are provided between the bearing and the bearing to seal grease inside the bearing, maintenance is free and the number of maintenance inspection items can be significantly reduced.

In addition, the above-mentioned embodiment described a configuration in which the conventional oil circulation type cylindrical roller bearing shown in Fig. 3 is changed to a grease-sealed type cylindrical roller bearing. It is also possible to change the sliding bearing of the type to a grease-sealed cylindrical roller bearing, and in this case, it is easy to change the shape by cutting the roll neck 3 from the form shown by the dashed line to the form shown by the solid line as shown in Fig. 1. It is possible to assemble grease-sealed cylindrical roller bearings.

〔effect〕

As described above, in the apparatus of the present invention, the ends of the cylindrical rollers located at both ends of the plurality of double-row cylindrical roller bearings, which are the main bearings that support the roll neck of the roll of the rolling mill, are placed on both ends of the roll neck in the axial direction. Because it is set so that it is located on the same vertical plane as both outer end faces of the chock, or as close to it as possible within a range that does not exceed this, the rated load of each bearing is greatly improved and there is no waste in the structure. (Also, since it has a grease-sealed structure with an oil seal between the guide ring and the inner ring, it is maintenance-free.

The present invention has excellent effects such as significant labor savings in inspection.

Note that other effects are substantially the same as those of the cylindrical roller bearing device shown in FIG.

[Brief explanation of the drawing]

FIG. 1 is a partial sectional view of the device of the present invention, FIG. 2 is a partial sectional view of a conventional oil film type sliding bearing device, and FIG. 3 is a partial sectional view of a conventional cylindrical roller bearing device. 1... Bank unroll 2... Barrel 3...
Roll neck 3a...The attachment is the root 3b...Large diameter shaft part 3c...Medium diameter shaft part 3d...Small diameter shaft part 3e...
・Shaft end 4...Chock 4a...Hole 4b, 4c
... Overhanging part 11.12 ... Double row cylindrical roller bearing
11a, 12a... Inner rings 11b, 12b... Outer rings 11c, 12c - Cylindrical rollers 11d, 12d... Cage 13... Double row tapered roller bearing 14... Spacer ring 15. 16... Guide Ring 17... Fillet ring 18... Rear cover 19... Thrust collar 20... Retaining ring 21... Front M 21a...
・Thrust housing 21b...Thrust cover patent Applicant: 1 person other than Sumitomo Metal Industries, Ltd.

Claims (1)

[Claims] 1. In a bearing device equipped with a plurality of double-row cylindrical roller bearings that support shaft portions of different diameters in a roll neck of a rolling roll in a chock, the double-row cylindrical roller bearing is a grease-filled bearing, Each inner ring has its respective end portions located on both end sides in the axial direction extending beyond both end faces of the chock on the same side, and the end faces of the cylindrical rollers located on both end sides in the axial direction extend beyond both end faces of the chock. Furthermore, each outer ring is provided with a guide ring at both ends in the axial direction for regulating the cylindrical rollers, and the guide ring and the inner ring 1. A bearing device for a roll of a rolling mill, characterized in that an oil seal for sealing grease is provided between the outer circumferential surface of an extending portion of the bearing device.