JPH03140620A - Bearing - Google Patents

Abstract

PURPOSE: To manufacture a bearing compactly and economically, by providing at least one recessed part having two circumferentially facing boundary walls in an outer race, and by tightly engaging a projection circumferentially fixed to a support member between the boundary walls. CONSTITUTION: Bearing outer races 6, 7 have two groove-shaped recessed parts 35 mutually facing in their diameter direction, and each recessed part 35 has two flat boundary walls 36 which radially extend and circumferentially face each other. Each end 34 (projection) of a cylindrical pin 33 is tightly engaged between the both boundary walls 36. A long groove 37 that extends in the axial direction and communicates with a supply hole 38 is drilled in a support hole 2 in a support member 1. Lubricating oil is sent from the supply hole 38 to the recessed part 35 through the long groove 37, and then sent to an non-illustrated rolling element inward in the radial direction. When the outer races 6, 7 relatively move slightly in the radially load direction, the end 34 of the cylindrical pin 33 slides along the radial boundary wall 36 of the recessed part 35.

Description

DETAILED DESCRIPTION OF THE INVENTION The invention relates in particular to a bearing of a shaft neck of a work roll of a rolling mill, as defined in the preamble of claim 1.

Bearings for the necks of rolling mill work rolls are known, of the type in which the outer ring of the bearing can rotate in a cylindrical support bore of a housing. However, this rotation is undesirable, especially in the case of rolling mill work roll bearings. This is because, during operation, one or more outer rings are displaced and vibrated in the circumferential direction within the support hole of the support member. The purpose of the present invention as characterized in claim 1 is that the vibration is caused by the accuracy of the rolled product, and the outer ring of the bearing is supported by an oil film in the support hole of the support member. Nevertheless, the object is to create a bearing of the above-mentioned type for a non-rotating type, in particular for the shaft neck of a working roll of a rolling mill. Furthermore, the bearing must be particularly compact and economical to manufacture.

In the case of the bearing according to the invention, the outer ring of at least one bearing, whether a sliding bearing or a rolling bearing, is installed in a support hole of a support member of the roll frame. The rotation of each outer ring within the support member is
This is blocked by a projection that engages a recess in the outer ring. In this case, each outer ring is supported in the radial direction via an oil film in the region of the load zone. Even when the shaft neck rotates at high speed, the shaft neck is supported vibration-free on the support member.

Furthermore, since plain bearings or rolling bearings with conventional operating dimensions can be integrated into the support member, the bearing according to the invention can be manufactured compactly and economically and can be easily combined with existing bearings according to the invention. can be exchanged for.

Advantageous embodiments of the invention are specified in claims 2 to 10.

The invention will be explained below with reference to illustrated embodiments.

In FIG. 1, a finishing roll pedestal (not shown)
The supporting member is indicated by 1. The support member has a cylindrical support hole 2 incorporating four rows of plane-symmetric tapered roller bearings. The tapered roller bearing is supported by the shaft neck 3 of the work roll 4.

Tapered roller bearings consist of two narrow roller bearings, each with a conical outer raceway.
It has two outer rings 5 and 6. Two narrow outer rings 5 of the bearing,
6, a wide outer ring 7 having a conical outer raceway of two conical rolling elements 8 is provided. The rolling elements 8 run on the inner tracks of two wide inner rings 9 placed on the axis g3.

The inner ring 9 is attached to the shaft neck 3, and the labyrinth seal 10 is attached to the working side.
and on the drive side by a nut 12 with an adjusting ring 11.

The outer ring 5, 6.7 surrounds the shaft neck 3 of the work roll 4 and is held on the work side by an inner flanged cover 14,
On the drive side, it is held by an outer flanged cover 13.

Each bearing outer ring 5, 6.7 has radial end faces 15 on both sides.

A spacer ring 16, which also has a radial end face 17, is installed between each narrow outer ring 5.6 and the wide outer ring 7 (FIG. 2).

An annular groove 19 is machined on each side of the cylindrical outer peripheral surface 18 of the outer rings 5, 6.7. Each annular groove 19 is provided with an elastic O-ring gasket 2o that laterally seals between the outer peripheral surface 18 and the support hole 2.

In the support hole 2 of the support member l, a narrow and shallow long groove 21 is machined between each two packings 20 of the outer rings 5, 6.7 and at the center of the load zone on the inner peripheral surface of the support hole 2. . That is,
The elongated groove 21 lies in a longitudinal plane transverse to the axis 27 of the shaft neck 3 and subjected to radial bearing loads (see direction 22).

A radial supply hole 23 is opened in each long groove 21 and communicates with a pressure oil passage 24 of a lubrication pump (not shown).

The load zone of the outer circumferential surface 18 further includes a section extending in the circumferential direction;
An oil distribution groove 25 is machined to uniformly distribute the lubricating oil supplied from the pump through the long groove 21 between the outer peripheral surface 18 and the support hole 2 of the support member 1.

That is, the outer peripheral surface 18 of each outer ring 5, 6.7 is at least partially supported by an oil film in the direction of the radial load in the support hole 2 of the support member l. In this case, the oil film may be a hydrostatic high-pressure oil film or a squeeze film.

In the case of this embodiment, since the pressure of the lubricating oil in the oil distribution groove 25 is high, a part of the lubricating oil reaches the outside through the gasket 20 and reaches the flanged cover 13 or 14 and the narrow outer ring 5 or 6. or through the bearing outer ring 5, 6 or 7.
and the spacer ring 16 to enter the inside of the tapered roller bearing and lubricate the rolling elements 8.

All end faces 15 of the outer rings 5.6.7 each have two diametrically opposed recesses 26 in a longitudinal plane extending in the direction of the arrow 22, transverse to the axis 27 of the axle neck 3. Each recess 26 has two boundary walls facing each other in the circumferential direction, and a projection fixed to the support member 1 in the circumferential direction is tightly engaged between the boundary walls.

In this example, the protrusion consists of one end 28 of a cylindrical pin 29. The other end 30 of the cylindrical pin 29 engages in an opposed recess 31 of the support member 1 or of a connecting element connected in a rotation-proof manner thereto.

The connecting elements consist of a flanged cover 13.14 on the axial outside of each narrow outer ring 5.6 and an associated spacer ring 16 on the inside.

Opposed recesses 31 are machined in the spacer ring 16 or the support member or in the end face 17 of the flanged cover 13, 14 and are axially opposed to the recesses 26, respectively.

One end 28 of each cylindrical pin 29 engages a recess 26 without play, and the other end 30 engages an associated opposed recess 31 with no play in the circumferential direction and with little play in the radial direction. That is, the outer rings 5.6.7 can be offset somewhat relative to each other in the direction of the radial load, without the cylindrical pin being overloaded or jammed in this case.

In FIG. 3, which shows another embodiment, the spacer ring 16 has two cylindrical opposed holes 32 passing through it in the axial direction. The two opposing holes 32 lie in a longitudinal plane extending in the direction of arrow 22 and are diametrically opposed. Each opposing hole 32 is provided with a cylindrical pin 33 having two opposing ends 34 projecting axially from the spacer ring 16 .

The bearing outer ring 6.7 has two groove-shaped recesses 35 that are diametrically opposed to each other. Each recess 35 has two radially extending and circumferentially opposing flat boundary walls 36 . Each end 34 of the cylindrical pin 33 is tightly engaged between the two boundary walls 36 .

The support hole 2 of the support member l has a supply hole 38 extending in the axial direction.
A long groove 37 that communicates with is machined. The lubricating oil is sent from the supply hole 38 to the recess 35 via the long groove 37, and then
It is fed radially inward to rolling elements (not shown).

A slight relative movement of the outer ring 6.7 on the oil film in the direction of the radial load causes the end 34 of the cylindrical pin 33 to slide along the radial inward direction 36 of the recess 35.

FIG. 4 shows an outer ring 6 of another embodiment. In this case, a cylindrical recess 39 and a shallow long groove 40 connected to the recess are machined into the outer peripheral surface 18 of the outer ring 6. The recess 39 is the outer ring 6
is located in the center of the load zone of the outer ring 6, so that it lies in a longitudinal plane extending across the axis of the shaft neck (not shown) in the direction of the radial load of the outer ring 6.

The recess 39 engages with a protrusion that is held against the support member l so as not to idle. In the case of this embodiment, the protrusion is the threaded portion 4
2 by the inner end 41 of a pin 43 which can be engaged with the outer circumferential surface 18. The pin 43 is connected to the support member l.
A hole 4 provided in the hole 4 and having a threaded portion 42 and extending in the radial direction
Accepted by 4.

Pin 43 has a central feed hole 45 with an outlet projecting into recess 39 at its inner end and connected to a source of high pressure oil (not shown). The outlet is provided on the inner end surface 46 of the pin 43.

The pin 43 is fully screwed into the threaded portion 42, and the end surface 46 is moved toward the bottom of the recess 39, and high-pressure oil flows between the end surface 46 and the bottom surface and between the support hole 2 and the outer peripheral surface 18. It is possible to form a restriction gap that restricts the flow rate. In this way, the predetermined rigidity of the oil film between the outer ring 6 and the support member 1 can be adjusted. The end 41 of the pin 43 has a recess 39 at the contact point.
is guided closely between the opposing boundary walls of the cylinder, and is lubricated by a portion of high-pressure oil.

In this embodiment, no or very little high pressure oil flows outwardly through the O-ring packing 20.

Therefore, the spacer ring 1 is attached to the rolling element (not shown).
Lubricating oil is supplied via a lubricating oil channel 47 which leads the lubricating oil inwardly by means of radial holes 48 at 6 .

The embodiments described above can be modified within the scope of the invention. Therefore, the outer ring of a sliding bearing can be used instead of the outer ring of a rolling bearing for the shaft support.

[Brief explanation of the drawing]

Fig. 1 is a partial vertical cross-sectional view of one embodiment of the bearing according to the present invention, and Fig. 2 is an enlarged view of the part indicated by A in Fig. 1 (however, the shaft neck, bearing inner ring, and rolling elements are 3 is a partial vertical sectional view of the bearing of the second embodiment (the shaft neck, bearing inner ring, and rolling elements are not shown), and FIG. 4 is a portion of the bearing of yet another embodiment. It is a longitudinal cross-sectional view (the shaft neck, bearing inner ring, and rolling elements are not shown). 1 is a supporting member, 5, 6.7 is an outer ring, 26° 35.39 is a recess, 28, 34.41 is a protrusion, and 36 is a boundary wall. 152-

Claims (10)

[Claims] (1) A bearing having a cylindrical outer circumferential surface supported by an oil film in the direction of radial load in the support hole of the support member and having at least one outer ring surrounding the shaft neck, the outer ring (5, 6, 7
) has at least one recess (26, 35, 39) with two circumferentially opposing boundary walls (36), between which there is a recess (26, 35, 39) with respect to the support member (1) A bearing characterized in that projections (28, 34, 41) fixed in the circumferential direction closely engage with each other. (2) The protrusion is located at one end (28) of the pin (29, 33, 43).
, 34, 41).The bearing according to claim 1, characterized in that it is formed by: , 34, 41). (3) characterized in that the opposite other end (30) of the pin (29) engages in the opposite recess (31) of the connecting element (13, 14, 16) fixed to the support member (1); The bearing according to claim 2. (4) At least one outer ring (5, 6, 7) on each side thereof
4. A bearing according to claim 1, wherein the radial end face (15) has at least one recess (26, 35) machined therein. (5) At least one of the recesses (39) is machined on the outer circumferential surface (18) of the outer ring (6), according to any one of claims 1 to 3. bearings. (6) The protrusions that engage with the respective recesses (35) on the outer peripheral surface (18) of the outer ring (6) are connected to the radial through holes (4) of the support member (1).
6. A bearing according to claim 5, characterized in that it is formed by the inner end (41) of a pin (43) which is incorporated in the outer circumferential surface (18) and is arranged to engage with the outer circumferential surface (18). (7) The pin (43) is indented (39) in the outer peripheral surface (18).
7. Bearing according to claim 6, characterized in that it has a central supply hole (45) with an outlet projecting inward and engaged with a source of pressure oil. (8) All the recesses (26, 35, 39) are the axial neck (3)
direction of radial loading (22) across the axis (27) of
8. Bearing according to claim 1, characterized in that it is arranged horizontally in a longitudinal plane extending to . (9) The one or more protrusions (30, 34, 41) are arranged to engage with each other without play in the circumferential direction and with play in the direction of the radial load. Bearing according to paragraph 8. (10) A bearing according to any one of claims 1 to 9, which has at least two outer rings disposed coaxially with each other in a support hole of a support member, Between both outer rings (5 or 6 and 7), projections (28, 34) are provided on both end faces (17) facing the outer rings (5, 6, or 7). 7
) is connected to the spacer ring (16) to prevent it from idling.
A bearing characterized in that it incorporates.