FI114166B - The bearing member - Google Patents

Description

11416 i

BEARING BODY

The invention relates to a bearing member having an outer ring bearing member 5 having a bearing housing 5 and an inner ring bearing member having an axis rotating with respect to each other, and barrel-like rolling members having two pivotable centering members

10

In applications where the shaft bearing is subjected to high radial loads and there is an angle error between the bearing and the shaft, a spherical roller bearing is generally used. Such applications include, for example, bearings of rolls 15 of a paper machine. In addition to the above features, the bearing carries significant axial loads in both directions. The spherical roller bearing has two barrel-shaped roller rows with curved rolling surfaces on the inside and outside of the bearing.

20 The spherical roller bearing requires sufficient radial load to operate. If there is play in the bearing, the rollers tend to decelerate with the unloaded part of the bearing. When the rollers return to the loaded part, the rollers and their rollers are rolling; '·· circumferential velocity difference between surfaces. The rollers are then accelerated very quickly by the shear forces to the bearing speed of the bearing rings. This may result in damage to the rolling surfaces. ···. if the lubrication of the bearing is poor. At worst, when the radial load is very low, the roll holder may also rotate! . ' misspeed to be too low. Also, when the axial load is high, the radial load may be too low on the second row of rollers. In this case, the aforementioned disadvantageous loading situation is created in the bearing, especially if the roller rows have separate holders. This situation is particularly common with large bearings with heavy rollers and their holders. To prevent this problem:: 5 paper machines have had to avoid certain line pressure ranges on rolls.

* ;. In some types of bearings, axial clamping members are used to eliminate the play between the rolling members and the 2 11416c pin faces. In double row bearings, axial displacement of the outer ring tightens one of the rolling members but at the same time loosens the second row. This will exacerbate the above problem.

5

It is an object of the invention to provide a bearing member which is resistant to load and shaft error and whose rolling members rotate despite the load on the bearing member. Characteristic features of the present invention will be apparent from the appended claims. In the bearing member according to the invention, the bearing clearance can be continuously adjusted as desired, whereby the rolling members rotate under all loading conditions. The play is preferably adjusted simultaneously in both roller rows. In this case, the bearing member operates as planned without artificially loading the shaft. In addition, the bearing member 15 adapts to the axial movement of the shaft despite high frictional forces.

The invention will now be described in detail with reference to the accompanying drawings, in which:

Fig. 1 is a cross-sectional view of an axially-free bearing of the invention having: an inner ring rotating and releasably mounted in a bearing housing;

Fig. 2 shows another embodiment of a bearing according to the invention in cross-section with the outer ring.

Figure 3 is a front elevational view of the bearing housing and seal pockets of the invention mounted thereon;

Figure 4 is a sectional view of a V · valve mounted in a duct extending into the pocket.

Figure 1 shows a bearing member 10 according to the invention, mounted on an axis 13 adapted to rotate. In the following description, the bearing member 10 is more simply referred to as a bearing.

Further, the components associated with the bearing housing 19 are schematically shown in Figures 11416c 3 without fastening means and seals. The rolling surfaces 16 and 16 'of the barrel-shaped roller members 15 of the embodiment of the double row spherical roller bearing are conventionally curved. According to the invention, the rolling surfaces 16 of the rolling members 15 formed on one of the bearing ring members 5 11 or 12 are arranged in two separate rings 18, 18 ', 18' '. In practice, the individual rings 18, 18 ', 18' 'are preferably divided vertically from the unitary ring, whereby the rolling surfaces 16, 16' correspond as closely as possible to the rolling members 15. In Figure 1, the rings 18 form the outer ring of the bearing 10 disposed in the bearing housing 14. Furthermore, the individual rings 18 are arranged to move axially relative to one another in the bearing housing 14. The preloading means included in the bearing 10 thereby removes or at least reduces In particular, the elimination of radial bearing play is important to the problem. As the radial clearance decreases, the rolling members 15 are continuously aligned with their rolling surfaces 16, 16 'and rotate normally, even though there is no load on the shaft 13.

20

The preloading means are adapted to continuously press the individual rings 18, 18 ', 18' 'in axially tightening direction against opposing forces. In this case, the bearing clearance in both bearing rows is removed simultaneously. In the embodiment of Figure 1, the preloading means 25 comprises two loading members 17 arranged symmetrically with respect to the bearing 10. The loading member 17 consists of an annular groove 20 disposed on the end and a sealing ring piston 22 sealed thereon. oil because the hydraulic 30 system provides sufficient axial force. For oil, a chamber 24 extends into the chamber 23 defined by the annular groove 20 and the piston 22, and the chambers 23 are supplied with oil produced by suitable means (not shown), which is continuously and preferably adjustable. By arranging. · 35 oil channels 24 of the loading members 17 together, applied by the same pressure, ··· both chambers 23, whereby both roller rows are loaded '! *. evenly. If necessary, the pressures in the chambers 23 may be different, whereby the position of the bearing 10 in the bearing housing 14 may be influenced. Spring means can also be disposed between the rings to push the rings 18 apart when the load pressure is reduced (not shown).

4

ViCl 5 The bearing of Fig. 1 can also be easily converted into a bearing where axial movement between the shaft and the inner ring is prevented. One possibility would be to arrange the threads on the shaft which, with the nut inserted, would press the inner ring against the shoulder on the shaft.

10

Further, as shown in Figure 1, there is relief between the individual rings 18 and the bearing housing 14. In general, there is a pocket 26 formed of a sealing circuit 32 between the two or at least one axially adapted ring and its support surface.

15 To the pockets 26, shown in more detail in Figure 3, lubricant is fed down the channel 27. Lubricant is kept separate from each other side surfaces of the loaded tire, the friction is reduced, and the tire movement is facilitated. Further, at the end of the pocket 26 of the channel 27, there is a valve 28 (Fig. 20 4) adapted to cut off the supply of the high pressure lubricating grease used as the lubricant when the grease layer reaches the desired thickness. Thus, the relief is axially movable: a static grease pad between the matched mating surfaces.

Preferably, the grease feed is continuous, but the channel 2 7 further includes a latch 25 to prevent the grease from leaving the pocket 26 through the channel 27. This will keep the pressure in the pocket 26 even when the fat supply is stopped. Instead of grease, the lubricant may also be an oil used for bearing lubrication.

Figure 2 shows an embodiment of a bearing member according to the invention, in which the shaft 13 remains stationary as the outer ring 31 attached to the housing 30 rotates. For functionally similar parts, the same reference numerals as above are used. Also in this embodiment, the axial movement of the shaft 13 can be prevented as described above. Bearing 10 is similar to the prior art. · But separate rings 18 'and 18' 'are disposed on shaft 13. Generally, preloading and relief is provided on a non-rotatable ring bearing member. In this embodiment, the load 114 "..: 5 insert member 17 is disposed between the rings 18 'and 18' ', requiring only one annular groove-piston assembly with a passage 24 for pressure medium. As before, the annular groove 20 has an annular piston 22. the piston 5 22 depresses the annular groove of the opposite ring Alternatively, between the rings 18 'and 18' 'there may be spring members forming preloading means (not shown) The structure is simple but preload is not adjustable.

10

Here, too, there is a relief between the individual rings 18 'and 18' 'and their support surfaces. To guide the grease into the pockets 26, the channels 27 with valves 28 and 29 are arranged on a shaft 13 which does not rotate.

15

In the examples, the ring bearing member against the individual rings is uniform. Alternatively, two separate but functionally connected spherical roller bearings may be used instead of a spherical roller bearing. However, in this case, the bearing door-20 assembly becomes remarkably wide, since the center of rotation of both roller rows must be arranged at the same position.

:: The preloading and relief according to the invention is suitable for bearings of almost any size. However, the biggest advantage is achieved with large and heavily loaded bearings. Pre-load despite high frictional forces and pre-tensioning '! reduces the likelihood of large and expensive bearings failing. In paper machines, for example, such bearings 30 have a diameter of up to 600 mm. Further, the axial movement of the bearing arrangement of the invention may be either free or blocked. Instead of the hydraulic preload, a spring V load may also be used.

Claims (11)

A bearing member (10), comprising an outer annular bearing member (11) with bearing housing (14) as supporting surface, and an internal annular bearing member (12) having the shaft (13) as supporting surface, which rotate in relation to each other, and thin-shaped rolling means (15) located in two rows between the bearing members (11, 12), the rolling means having the same center of rotation and whose curved rolling surfaces (16, 16 ') are formed in the said ring bearing members (11, 12), characterized in that the rolling surfaces (16) in the rolling member (15) formed in one of the ring bearing members (11, 12) are arranged in two separate rings (18, 18 ', 18' ') arranged to move axially in relation to each other, and the bearing member (10) includes preload devices for axially pushing each of the separate rings (18, 18 ', 18' ') in axially pulling direction to remove the bearing spool. Bearing means (10) according to claim 1, characterized in that 2. at least one of the load means (17) included in the preload devices consists of a ring lock (20) formed on the end surface and a ring piston sealed thereon (20). (22), which * is arranged to be operated with a pressure medium. '*. * 25 Bearing means (10) according to claim 1 or 2, characterized in that the load means (17) are arranged symmetrically in V, relative to the separate rings (18) and that feeds ·. (24) of printing medium until these are joined together. ·; · 30 Bearing means (10) according to any of claims 1-3, characterized in that the separate rings (18) are arranged in a bearing housing (14). • · ·; t Bearing means (10) according to claim 1 or 2, characterized in that the separate rings (18 ', 18' ') are arranged on the shaft (13). 9 114 Ί 6 c Bearing member (10) according to claim 5, characterized in that the load member (17) consists of a ring lock (20) and a sealing ring piston (22) arranged in one of the separate rings (18 ', 18' '), which is arranged to correspond to the other 5 of the separate rings (1818 ''). Bearing means (10) according to any one of claims 1-5, characterized in that the preload devices comprise the spring means arranged between the separate rings (18, 18 ', 18' '), which are arranged to disassemble the separate rings (18). , 18 ', 18' '). Bearing means (10) according to any one of claims 1-6, characterized in that between the bed or only one of the various rings (18, 18 ', 18' ') arranged axially movable and its supporting surface is one of the sealing circuit (32) formed pocket (26), to which a channel (27) extends for conducting lubricant into said pocket (26). Bearing means (10) according to claim 8, characterized in that at the end of the channel (27) bordering the pocket (26) there is a valve (28) arranged to close the supply of · 1 "lubricant when the lubricant layer has pretty desired thickness. »· · • · ·» · Bearing means (10) according to any one of claims 1-6, characterized in that the corresponding bearing bearing means (Y) is responsive to the different rings (18, 18 ', 18' '). Bearing means (10) according to any one of claims 1-6, characterized in. 30, characterized in that the ring bearing member consists of two separate and functionally connected rings against the different rings (18, 18 ', 18' '). • 1 · »I · *» »