JPS61256021A - Multiple roller bearing - Google Patents

Abstract

(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

DETAILED DESCRIPTION OF THE INVENTION Field of the Invention The present invention relates to bearings. More specifically, the present invention is a novel multi-row bearing incorporating tapered rollers.

BACKGROUND OF THE INVENTION During the operation of rolling mills, such as those used in the steel industry, vast amounts of water are often used for cooling purposes. Because of the high forces involved in rolling mill operation, roller bearings are lubricated with common oil-based lubricants.

To operate at maximum efficiency, it is essential to keep roller bearings free of water and other foreign objects.

Seals and seal positioning are very important to keep contaminants out of the bearings in the rolling mill. One seal arrangement that protects common roll neck bearing arrangements is located far away from the bearing and is often scratched when the roll is removed for regrinding and then placed back in place. occurs frequently as far as work roles are concerned. An example of a conventional roll neck bearing configuration in which the seal is far from the bearing is the A.G. Beatross (A.

No. 3,512,855, entitled "Water and Lubricating Oil Seal Means for Rolling Mills," issued to J.

In other conventional roll neck bearing configurations, the seals that keep the bearing free of contaminants are housed in an end ring that is separate from the outer race of the bearing. An example of such a configuration is Gerhard Reiter.
U.S. Patent No. 4.255.485 ``Unitized Multi-Row Tapered Roller Bearing'' granted to Akio Aoki et al. on November 25, 1919GO and U.S. Patent No. 4.255.485 granted to Akio Aoki et al. on December 27, 19G3. 11th. li 22.6
No. 98 "Bearing Assemblies".

Problems to be Solved by the Invention Accordingly, an object of the present invention is to provide a seal for a bearing for a rolling mill that is not damaged by removal and reassembly of the roll during regrinding of the roll. ◇ An elegant way to solve the problem is to provide a sealing arrangement that is integral with the component. Briefly, the new multi-row bearing has a pair of intermediate raceways and a pair of end raceways. and an outer race means having a pair of intermediate tracks surrounding an intermediate track of the inner race means and a pair of end tracks surrounding an end track of the inner race means, each track on the outer race means It surrounds and accommodates different tracks on the inner race means.

Rollers are arranged in rows between corresponding tracks of the inner and outer race means, with different rows of rollers between corresponding intermediate and end tracks of each set. One end seal is fitted within the annulus between the inner and outer race means adjacent each end of the annulus. The end seal is shaped to fit completely within the annulus. Each end seal has an elastomeric portion that cooperates with the inner race means to form a barrier across the ends of the bearing.

The inner race means may include a pair of inner races, each inner race bearing with one intermediate raceway and one end raceway. The inner end surfaces of the inner races may be butt-joined directly together, or alternatively, spacers may separate the inner races. When the inner end surfaces of the inner races contact each other, means are provided for sealing the contacting inner end surfaces of the inner races. Spacer if the inner races are separated by a spacer? Means for sealing is provided.

DESCRIPTION OF THE PREFERRED EMBODIMENTS Referring to the exemplary drawings, and more particularly to FIG. 1, there is shown a multi-row tapered roller bearing particularly suited for positioning and supporting the entire work roll or support roll 12 of a rolling mill. Each roll 12 of the rolling mill has a roll neck 1 at its end.
4, these are the reduced diameter end portions, and each roll neck 14 is received in a bearing. For bearings,
It is tightly held in a chock 16 that is fixed to the frame of the rolling mill. In chock 16,
Contains a conventional retaining device and is further provided with a conventional O-ring seal 1g and a seal O.
This bearing allows the roll 12 to rotate within the chock 16.

This bearing is provided with inner race means having a pair of inner races 2o and 22. The holes in inner races 2o and 22 have the same diameter and the diameter of the hole is approximately the same as roll neck 14, so roll neck 14 fits through the holes in inner races 2o and 22. Preferably, the hole in the inner race is slightly larger in diameter than the diameter of the roll neck Ill to provide a loose fit to facilitate bearing removal.

The inner races 20 and 22 are truncated and have laterally extending distal end faces 24 and 26, respectively.

There are four inclined tracks 2g between the two end faces 21I and 26,
30.52 and 514 are provided. Inner races 20 and 22 provide the bearing with intermediate races 3° and 52 and end races 2g and 51 Jl, respectively. The two intermediate tracks 30 and 52 are separated by an annular spacer 56.

The end track 28 and intermediate track 5o of the inner race 20 are the track 2
8 and 30 are separated by a cylindrical intervening surface 3g following the larger diameter ends.

The intermediate raceway 2 and the end raceway 311 on the inner race 22 are separated by a cylindrical intervening surface IIO which follows the larger diameter ends of the races 52 and 514. The tracks 28 and 30 taper radially inwardly from the cylindrical intervening surface 3g. Tracks 32 and 51+ taper radially inwardly from a cylindrical intervening surface lIO.

inner races 20 and 22 are split outer race 112;
Surrounded by outer race means including ll11 and 116i. Outer race 42 is axially separated from outer race 1III by an annular spacer 118. Outer race ll1l is axially separated from outer race lI6 by an annular spacer 50.

The outer race lII+ has races 52 and 511, thereby giving the bearing an opposing intermediate raceway to the corresponding intermediate races 30 and 52 on the inner races 20 and 22, respectively. Two intermediate tracks 52 and 51 on outer race 44
+ are separated by a cylindrical intervening surface 56 that follows the larger diameter ends of tracks 52 and 54. Raceways 52 and 51+ taper radially outward from a cylindrical intervening surface 56.

The end track 5g in the outer race 42 is the outer race l+2
tapers radially outwardly from the outer end of the inner race 20 and is mounted oppositely around the corresponding end raceway 28 of the inner race 20. The end raceway 60 of the outer race 46 tapers radially outwardly from the outer end of the outer race li6 and is opposed and attached to the corresponding end raceway 6 of the inner race 22.

There is one row of tapered rollers 62 between corresponding end raceways 28 and 58, and similarly, there is another row of tapered rollers 61I between intermediate raceways 50 and 52;
There is still one more row of tapered rollers 66 between the end raceways 54 and 60, and one more row of tapered rollers 68 between the end raceways 54 and 60.

Appropriate circumferential spacing between individual rollers in each of the four rows is maintained by cages. The separate cages 70 for any row of rollers are separate from each other and may be made of plastic or any other suitable material.

The two retainers serve as intermediate retainers corresponding to the intermediate raceways in the main bearing, and the other two retainers serve as end retainers corresponding to the end races in the present bearing.

1 and 2, it can be seen that end seals are fitted into the annular portion 72 between the inner and outer race means adjacent the ends of the annular portion. Is each end sealed in a sealed case? 4 and annular nidistoma part 7
It is equipped with 6. A separate large spring 7g ensures that the nisttomer portion 76 contacts the outer diameter extension 80 of the inner race.

+ and outer race lI on the axial outer surface 2 of the inner race 20
The axially outer surface 82 of No. 2 is the shaft #'! of the bearing. It extends along the same cross section passing through r. The end seal is shaped to fit completely within the annulus 72. Seal case 711 has a generally C-shaped cross-section, with the vertical portion of the C-shape lying generally along the same transverse plane as the outer surfaces 211 and 82 of inner race 20 and outer race 112, respectively. The horizontal portions of the C-shaped seal case are a generally axially extending radially outer portion 83 and a generally axially extending radially inner portion 8il. Elastomer portion 76
is attached to the axially extending portion 8I+.

Although the crossbar of each roller retainer 70 is tilted,
The holes 86 in the edges of the small I diameter crossbar are larger than the outside diameter of the adjacent portion of the inner race means. The axially extending portion 81+ of the seal case is connected to the hole 8 of the retainer 70.
It extends into 6.

In the embodiment of FIG. 2, the seal case has an outer race li
It is formed on the inner surface of 2 and is firmly held in the deep recess. The seal case is pressed into the deep recess by a brace fit by being inserted from right to left as viewed in FIG. 2 into the end seal case bore.

In the embodiment of FIG. 5, the end seal is sealed in seal case 7II.
The annular portion 72 between the inner and outer race means is retained by a molded annular rubber bead 92 on the outer diameter of the overlying elastomer 93. The rubber bead is the outer race 4
It extends into an annular groove 911 on the inner surface of 2. The annular groove 9' is axially spaced from the end face 82.

The end seal is inserted into the annular portion 72 by pressing the end seal into the annular portion 72 from right to left as viewed in FIG.

In the embodiment of FIG. 4, the metal portion of the end seal is coated with rubber to ensure a positive seal.

The mechanical holding force is 9 g of the groove formed in the outer race 42.
It is provided by bending the outer portion of the section 83 which extends generally axially into the .

In the embodiment of FIG. 5, the sealing case has nine radially outer portions 100 covered with beveled rubber. A deep groove 9 with a correspondingly sloped surface is formed on the inner surface of the outer race.

The end seal is installed by inserting it into the annulus between the inner and outer race means from left to right as viewed in FIG. The direction of installation is such that the sealing case bends its outer surface inwardly past a smaller surface 1011 than itself and then pops into the final position shown in FIG. 5 past shoulder 102. Do it like this.

In the embodiment of FIG. 6, the end seal case includes a radially extending portion 105 integral with portion 85 and a portion 106 extending axially away from shoulder 102 and parallel to portion 85.
I have everything. A plurality of circumferentially spaced ears 108 (only one shown in factor 6) are preformed to form retention ears. The seal case is rubber coated at 110. Pre-bending the ears 108 outwardly imparts positive residual strain energy to the ears so that the ears spring back into the grooves 98 as the retaining ears pass through the shoulder 112t. The rubber sheath 110 and case are configured to seal the surfaces while applying a positive compressive force to force the retaining ears into the outer race grooves 98.

The spacer 56 shown in FIG. 1 also seals contaminants from entering the space between the inner ends of races 20 and 22. The seal arrangement for spacer 56 of FIG. 1 is shown in more detail in FIG. 11. 11, O-rings 1111 and 116 are fitted into annular grooves 118119 formed in inner end surfaces 120 and 122 of inner races 20 and 22, respectively.

In the spacer sealing arrangement shown in FIG. 7, deep grooves are formed in the inner end faces 128 and 130 of inner races 20 and 22, respectively.

Side 1 U2 and 151 of the deep hole! and the inner surface 1110 of the spacer 36 is such that the elastomer 142
An annular space is formed to receive a sealing member made of an annular member having a shape of 11+. Ring seal 11 & 5 and 1
117 is in contact with the bottom surfaces 1119 and 151 of the deep bore.

In the spacer sealing means shown in FIG. 1, the spacer includes a central hole and deep bores extending from both ends of the spacer at a west longitude larger than the central hole to provide an annular space with a U-shaped cross section. A U-shaped annular elastomeric seal 150 is confined within the annular space.

In the spacer sealing means shown in FIG.
Hole 6 is larger than the hole through races 20 and 22.

This sealing member includes an annular elastomer 155 molded around a gold layer ring 155. Lip seals 157 and 159 form part of elastomer 153 and engage races 20 and 22, respectively.

For some rolling mill bearings, a spacer may not be included as part of the inner race means. In such a case, the inner end surfaces of the inner races should abut and some means should be provided to seal the abutting inner end surfaces of the inner races. Different means of sealing the abutting ends of the inner races are shown in FIGS. 8, 9 and 10.
12 and 15. Referring to FIG. 8, the mating end surfaces 1 of the inner races 20 and 22
52 and 151+ are fitted into adjacent deep counterbores 158 and 160 formed in the inner end surfaces of inner sides L'-720 and 22, respectively. A central rectangular metal band 162 completely surrounded by elastomer strengthens the seal. Lip seals 1611 and 166 are provided on opposite sides of the seal.

The lip seals are in contact with the bottom surfaces of deep grooves 158 and 160.

In the embodiment of FIG. 9, an accordion-shaped seal 170 is confined within a deep bore 172 formed in inner race 22. In the embodiment of FIG. A deep hole 1 of the inner race 22 is formed in the inner race 20 with a diameter larger than that of the deep hole 172. An annular projection 176 on the inner surface of the inner race 22
The surface of the protrusion is complementary to the surface of the deep bore 1711 and extends into the deep bore 51711 of the inner race 20.

In the sealing means of the embodiment of FIG. 10, the seal includes an annular elastomeric seal 180t having an inverted U-shaped cross section. An annular metal band 1g2 is attached to the edge of the seal.

In the embodiment of FIG. 12, deep grooves IB and 186 are formed on the inner end surfaces of inner races 20 and 22, respectively.

Bottom tag and 1 of deep part 1gl+ and 186 respectively
90, the deep end of the deep bore is inclined radially inward from the shallow end of the deep bore. An elastomer seal with an inverted V-shaped cross section is enclosed in a deep counter seat. A metal band of triangular cross section is placed within the groove of the inverted V-shaped seal.

In the embodiment of FIG. 13, the seal comprises a metal band 200 completely surrounded by an elastomeric annular member 202. In the embodiment of FIG. Elastomeric annular member 202 includes an inner race 22
There is a complementary radially outer surface 2011 on the side of the deep groove 206.

The annular member 202 also includes a bottom 210 of the deep bore 201+.
There is a complementary radially extending end surface 208 . This annular member has a deep counterbore 2 on the inner end surface of the inner race 20.
There are a pair of integral annular open lips 212 and 211+ that sealingly join the bottom surface 216 of the 18.

Effects of the Invention In the bearing of the invention, the end seal is not attached to a separate ring, and the end seal is not far from the bearing itself. Rather, the end seal is placed in the annulus between the inner and outer races.

Because the present invention does not require a separate ring to accommodate the end seals, the present bearing assembly is inexpensive to manufacture and is described in US Pat. No. 4,255,1111! It performs the same operation with fewer parts than bearing assemblies such as those shown in No. 5 and No. 4.1122.698.

Bearings of the Invention Also patents featuring separate end rings to support the end seals and bearings disclosed in patents such as U.S. Pat. It is constructed in such a way that it requires much less longitudinal space compared to the longitudinal space required for the product, yet still maintains the same performance as the bearings disclosed in the above-mentioned patents.

[Brief explanation of the drawing]

FIG. 1 is a partial sectional view of a roll of a rolling mill, the neck of the roll projecting into a chock in the frame of the rolling mill and supported within the chock by the multi-row bearing of the present invention; 2 is a partial sectional view showing one embodiment of an end seal of the present invention; FIG. 5 is a partial sectional view showing another embodiment of an end seal of the present invention; FIG. 5 is a partial sectional view showing still another embodiment of the end seal of the present invention; FIG. 6 is a partial sectional view showing still another embodiment of the end seal of the present invention; FIG. FIG. 7 is a partial cross-sectional view showing another embodiment of the sealing means when used to separate two inner races of spacer metalwork. 8 is a partial sectional view showing an example of the sealing means when the inner end surfaces of two inner races are butt-jointed together; FIG. 9 is a partial sectional view showing the inner end surfaces of two inner races. Fig. 10 is a partial sectional view of another embodiment of the sealing means when the inner end surfaces of the two inner races are butt-jointed together; FIG. 11 is a partial cross-sectional view of another embodiment of the sealing means when the two inner races are separated by a spacer; FIG. 12 is a partial cross-sectional view of the two inner races; FIG. 15 is a partial cross-sectional view of yet another embodiment when the end faces are butt-jointed together; FIG. 15 is a further embodiment of the sealing means when the inner end faces of the two inner races are butt-jointed together; FIG. 111 is a partial cross-sectional view of another embodiment of the sealing means when the two inner races are separated by a spacer; FIG. 15 is a partial cross-sectional view when the two inner races are separated by a spacer; FIG. 6 is a partial cross-sectional view of another embodiment of the sealing means when

Claims (1)

[Claims] 1. An inner race means having a pair of intermediate tracks and a pair of end tracks, a pair of intermediate tracks surrounding the intermediate track of the inner race means, and a pair surrounding the end tracks of the inner race means. an outer race means having end races, each raceway on the outer race means correspondingly surrounding a different raceway on the inner race means to create an annular portion between the inner race means and the outer race means; and the inner race means includes rollers arranged in rows between corresponding raceways of the outer race means, with different rows of rollers between corresponding intermediate and end races of each set. a row bearing having an end seal fitted within the annular portion between the inner race means and the outer race means adjacent each end of the annular portion, each end seal being configured to fit completely within the annular portion; A multi-row bearing characterized in that it is made and has a portion of elastomer that cooperates with the inner race to form a barrier at the end of the bearing. 2. A multi-row bearing as claimed in claim 1, wherein each end seal is press fit into the annular portion between the inner race means and the outer race means. 3. The inner surface of the outer race means has a groove spaced axially from each end thereof, and the axial retaining portion of each end seal ends in the annulus between the inner race means and the outer race means. A multi-row bearing according to claim 1, characterized in that it fits into a groove to retain the seal. 4. Separate intermediate roller cages and end roller cages circumferentially separate the rollers in each row, with each roller cage being pulled apart from each other and each end roller cage being separated from adjacent portions of the inner race means. Claim 1, further comprising a hole in the outer edge of a diameter greater than the outside diameter, with the elastomer portion of each end seal extending into the hole in the corresponding end roller cage. Multi-row bearing. 5. A multi-row bearing comprising a pair of inner races each having an intermediate raceway and an end race, said intermediate raceway being separated by a spacer, means for sealing said spacer, and said inner race having said intermediate raceway separated by a spacer; outer race means having a pair of intermediate tracks surrounding an intermediate track of the race means and a pair of end tracks surrounding an end track of the inner race means, each track of the outer race means having a different track of the inner race means; and correspondingly surrounding and providing an annular portion between the inner and outer race means, and rollers disposed in rows between corresponding tracks of the inner and outer race means. There are different rows of rollers between the corresponding intermediate raceway and end raceway of each set, and further comprising end seals forming a barrier at both ends of the annulus between the inner race means and the outer race means. A multi-row bearing characterized by: 6. A multi-row bearing according to claim 5, wherein the means for sealing the spacer comprises an O-ring received in an annular groove in the inner end face of each inner race. 7. The spacer has a hole of a larger diameter than the hole in the inner race, a portion of each inner end surface extending radially inwardly from the surface of the hole in said spacer to provide an annular space, and a sealing member in said annular space. A multi-row bearing according to claim 5, characterized in that it is confined. 8. The spacer has a central hole and a diameter larger than the central hole;
Claims characterized in that the spacer has a counterbore extending from each end creating an annular space having a U-shaped cross-section, and an annular seal having a U-shaped cross-section is confined within the annular space. Row bearing as described in paragraph 7. 9. A multi-row bearing having a pair of inner races each having an intermediate raceway and an end race, the inner end surfaces of the inner races being butt-joined to each other, the joint inner end surfaces of the inner races being sealed. and an outer race means having a pair of intermediate tracks surrounding an intermediate track of the inner race means and a pair of end tracks surrounding an end track of the inner race means, each track on the outer race means being a different track of the inner race means. rollers correspondingly surrounding the raceways and adapted to provide an annulus between the inner and outer race means and arranged in rows between corresponding tracks of the inner and outer race means; having a different row of rollers between the corresponding intermediate raceway and end raceway of each set, and further comprising end seals forming a barrier at each end of the annulus between the inner race means and the outer race means. A multi-row bearing characterized by: 10. The means for sealing the joint inner end surfaces of the inner races comprises a counterbore in the inner end surface of each inner race and a seal fitted within the counterbore. Each row of bearings listed in section. 11. The multi-row bearing according to claim 10, wherein the seal is an accordion type seal. 12. The multi-row bearing of claim 10, wherein said seal encloses a metal band therein. 13. A multi-row bearing according to claim 10, characterized in that the seal is of inverted U-shaped cross-section and an annular metal band is placed in the groove of the seal. 14. In an elastomeric annular member, said seal having a surface in sealing contact with a side wall of a counterbore on an inner end surface of one inner race and a second surface in sealing contact with a bottom surface of said counterbore. the elastomeric annular member having an integral annular open lip in sealing engagement with the bottom surface of a counterbore on the inner end surface of the other inner race; A multi-row bearing according to claim 10.