JP2020159523A - Bearing device - Google Patents

Abstract

To provide a bearing device which suppresses abrasion and galling caused by a contact between an inner ring or an outer ring and a cylindrical roller of a cylindrical roller bearing, and which prevents breakage of a cylindrical roller bearing which starts at the place where these have occurred.SOLUTION: A bearing device 23 includes: a first bearing 31 comprising a cylindrical roller bearing which includes an inner ring 34, an outer ring 35 arranged opposing to the radially outside of the inner ring 34, and a plurality of cylindrical rollers 36, 37 arranged between the inner ring 34 and the outer ring 35, and for receiving only a radial load; and a second bearing 32 arranged between the inner ring 34 and the outer ring 35, and for receiving only an axial load.SELECTED DRAWING: Figure 3

Description

The present invention relates to a bearing device used for a pallet carriage or the like in a sintering facility.

Patent Document 1 discloses a bearing for a pressure roller used for a pallet carriage in a sintering facility. This sintering facility is a facility in which the raw materials loaded on the pallets are baked and hardened in a furnace while running on rails in a state where about tens to hundreds of pallet carts are connected in a ring shape. On the lower surface of the pallet carriage, wheels traveling on the rail and bearings for pressure rollers in which the sprocket driving the traveling of the pallet carriage mesh with each other are provided coaxially.

Since a shocking load is applied to the pressure roller bearing when the sprockets mesh with each other or when the hardened raw material is discharged, a cylindrical roller bearing with high load capacity and outer ring strength is adopted. There is.

Not only the radial load when the sprockets mesh with each other, but also the axial load is applied to the bearing for the pressure roller due to the wear of the sprockets, the misalignment of the equipment, and the like. Since such an axial load is applied by contacting the flange portion formed on the inner and outer rings with the end face of the cylindrical roller, wear and galling are likely to occur on the collar portion and the end face of the cylindrical roller. In the technique described in Patent Document 1, a coating is applied to the flange portion of the inner and outer rings and the end face of the cylindrical roller in order to prevent the occurrence of wear and galling due to the axial load and the damage of the inner and outer rings starting from these points. The slidability when they come into contact with each other is enhanced.

Japanese Unexamined Patent Publication No. 2014-145443

In recent years, in this type of sintering equipment, the number of pallet carriages and the load capacity have tended to increase, and the axial load applied to the bearings for pressure rollers has also increased. Since the technique described in Patent Document 1 only forms a film on the flange portion of the inner and outer rings and the end face of the cylindrical roller, it does not prevent contact between the two, and therefore, there is a limit in dealing with an increase in axial load.

An object of the present invention is to provide a bearing device capable of suppressing an axial load from being applied to a cylindrical roller bearing and preventing damage to the cylindrical roller bearing.

(1) The bearing device of the present invention is a cylindrical roller bearing including an inner ring, an outer ring arranged so as to face the radial outer side of the inner ring, and a plurality of cylindrical rollers arranged between the inner ring and the outer ring. The bearing is composed of a first bearing and receives only a radial load, and a second bearing arranged between the inner ring and the outer ring and receiving only an axial load.

According to this configuration, the first bearing composed of cylindrical roller bearings receives only the radial load applied to the bearing device, and the second bearing receives the axial load, so that the axial load is applied to the first bearing. It is possible to suppress wear and galling of the inner and outer rings and the cylindrical roller, and prevent damage to the first bearing starting from the place where these occur.
In addition, in the above, "cylindrical roller" is a general term for rollers formed in a cylindrical shape (cylindrical shape), and also includes needle-shaped rollers and rod-shaped rollers.

(2) Preferably, the bearing device is used for a pressurizing roller of a pallet carriage in a sintering facility, and the second bearing is a ball bearing capable of applying an axial load.
With such a configuration, the axial load applied to the outer ring or the inner ring of the first bearing can be received by the second bearing.

(3) Preferably, the second bearing is a slide bearing capable of applying an axial load.
With such a configuration, the axial load applied to the outer ring or the inner ring of the first bearing can be received by the second bearing. Further, the second bearing can be easily incorporated between the outer ring and the inner ring of the first bearing.

(4) Preferably, the second bearing is elastically deformable in the axial direction.
With such a configuration, it is possible to reduce the impact when an axial load is applied by the second bearing.

(5) Preferably, a radial gap is formed between the second bearing and the outer ring or the inner ring.
With such a configuration, it is possible to prevent a radial load from being applied from the inner ring or the outer ring of the first bearing to the second bearing.

(6) The cylindrical rollers of the first bearing are arranged in a double row, and the second bearing is arranged between the axial directions of the cylindrical rollers in the double row.
With such a configuration, the second bearing can be arranged by utilizing the space between the cylindrical rollers arranged in the double row, and the increase in size of the bearing device due to the provision of the second bearing can be suppressed. Can be done.

(7) Preferably, the second bearing is arranged at the axial end of the first bearing.
With such a configuration, the second bearing can be easily incorporated between the inner ring and the outer ring in the first bearing.

According to the present invention, it is possible to suppress wear and galling due to contact between the flange portion of the inner ring or outer ring of the cylindrical roller bearing, which is the first bearing, and the end face of the cylindrical roller, and prevent damage to the first bearing. it can.

It is a schematic side view of the sintering equipment to which the bearing apparatus which concerns on 1st Embodiment of this invention is applied. It is sectional drawing which shows the traveling part of the pallet carriage. It is sectional drawing of the bearing for a pressure roller. It is sectional drawing of the bearing apparatus which concerns on 2nd Embodiment of this invention. It is sectional drawing which shows the 2nd bearing in the 2nd Embodiment enlarged.

Hereinafter, embodiments of the present invention will be described with reference to the drawings.
[First Embodiment]
FIG. 1 is a schematic side view of a sintering facility to which the bearing device according to the first embodiment of the present invention is applied. The sintering facility 10 includes a pallet carriage 11, rails 12, a driving sprocket 13, a driven sprocket 14, and an ignition furnace 15.

The pallet carriage 11 includes a pallet 11a that houses iron ore and limestone that are raw materials for sinter, and a traveling portion 11b provided on the lower surface of the pallet 11a. Hundreds of pallet carts 11 are connected in an annular shape and are wound around a driving sprocket 13 and a driven sprocket 14. The pallet carriage 11 circulates in the direction of arrow A at an extremely low speed by being driven by the drive sprocket 13.

The rail 12 is arranged between the driving sprocket 13 and the driven sprocket 14. The traveling portion 11b of the pallet carriage 11 travels on the rail 12.
The drive sprocket 13 and the driven sprocket 14 support the pallet carriage 11 by engaging with the traveling portion 11b of the pallet carriage 11. The drive sprocket 13 is rotated by a drive unit such as a motor (not shown). The driven sprocket 14 rotates as the pallet carriage 11 circulates and moves by the drive sprocket 13.

The ignition furnace 15 is provided corresponding to the pallet carriage 11 on the upper stage side between the driving sprocket 13 and the driven sprocket 14. The ignition furnace 15 heats the raw material housed in the pallet carriage 11 and hardens it to produce sinter. The pallet carriage 11 discharges sinter when tilted along the circumference of the driven sprocket 14.

FIG. 2 is a cross-sectional view showing a traveling portion 11b of the pallet carriage 11.
The traveling portion 11b includes an axle 21, wheels 22, and a bearing for a pressure roller 23.
The axle 21 is rotatably supported on the lower surface of the pallet 11a of the pallet carriage 11.
The wheel 22 has a bearing portion 25 and a wheel body 26. The bearing portion 25 is a double row tapered roller bearing. The bearing portion 25 has an inner ring 25a, an outer ring 25b, and a plurality of tapered rollers 25c. The inner ring 25a of the bearing portion 25 is fitted to the outer peripheral surface of the axial end portion of the axle 21 and fixed to the axle 21.

The wheel body 26 is formed in a cylindrical shape. The inner peripheral surface of the wheel body 26 is fitted to the outer ring 25b of the bearing portion 25 and fixed to the outer ring 25b. The outer peripheral surface of the wheel body 26 comes into contact with the upper surface on the rail 12. A flange portion 26a protruding outward in the radial direction is provided at an axial end portion of the wheel body 26. By engaging the flange portion 26a with the side surface of the rail 12, the wheel 22 is prevented from coming off.

FIG. 3 is a cross-sectional view of a bearing for a pressure roller. In the following description, the left side of FIG. 3 is referred to as one side in the axial direction, and the right side is referred to as the other side in the axial direction.
The pressure roller bearing 23 corresponds to the bearing device of the present invention, and includes a first bearing 31 and a second bearing 32.

The first bearing 31 is a double row cylindrical roller bearing. Further, the first bearing 31 is a full roller bearing without a cage. The first bearing 31 includes a first inner ring 34, a first outer ring 35, and cylindrical rollers 36 and 37. The first inner ring 34 is formed in a cylindrical shape. Two rows of inner tracks 34a and 34b are formed on the outer peripheral surface of the first inner ring 34.

The first inner track 34a arranged on one side in the axial direction (left side in FIG. 3) is wider in the axial direction than the second inner track 34b arranged on the other side in the axial direction (right side in FIG. 3). It is formed.
On one side of the first inner track 34a in the axial direction and on the other side of the second inner track 34b in the axial direction, a first flange portion 34c projecting outward in the radial direction is provided. Further, a second flange portion 34d protruding outward in the radial direction is provided between the first inner track 34a and the second inner track 34b.

The first and second flanges 34c and 34d restrict the axial movement of the cylindrical rollers 36 and 37 on the first and second inner trajectories 34a and 34b. An oil passage 34h for filling grease is formed in the flange portion 34d, and the first bearing 31 is configured so that grease can be filled between the first inner ring 34 and the first outer ring 35 in the radial direction. Has been done.

At the end of the first inner ring 34 on the other side in the axial direction (right side in FIG. 3), a small diameter portion 34e having an outer diameter smaller than that of the first flange portion 34c and the second inner track 34b is formed. A second bearing 32 and a seal member 39a, which will be described later, are attached to the small diameter portion 34e.

The cylindrical rollers 36 and 37 are composed of a first cylindrical roller 36 and a second cylindrical roller 37. The first cylindrical roller 36 is arranged on the first inner track 34a. The second cylindrical roller 37 is arranged on the second inner track 34b. The first cylindrical roller 36 is formed to be longer in the axial direction than the second cylindrical roller 37.

The first outer ring 35 is formed in a cylindrical shape. An outer track 35a is formed on the inner peripheral surface of the first outer ring 35. The outer track 35a is arranged so as to face the radial outer side of the first and second inner tracks 34a and 34b. Both the first cylindrical roller 36 and the second cylindrical roller 37 are arranged on the outer track 35a. The outer track 35a has a constant inner diameter. Therefore, the outer orbit 35a and the first cylindrical roller 36 and the second cylindrical roller 37 can move relatively in the axial direction.

As shown in FIG. 2, the driving sprocket 13 and the driven sprocket 14 mesh with the outer peripheral surface of the first outer ring 35. At this time, a radial load is applied to the first outer ring 35. Further, as shown in FIG. 1, the radial load is also applied to the first outer ring 35 by the pallet carriage 11 tilting along the driven sprocket 14 and colliding with the preceding pallet carriage 11. Due to wear of the driving sprocket 13 and the driven sprocket 14, misalignment of the equipment, and the like, not only the radial load but also the axial load is applied to the first outer ring 35.

Of these, the radial load is applied from the first outer ring 35 to the first and second cylindrical rollers 36 and 37 and the first inner ring 34. That is, the first bearing 31 receives a radial load. On the other hand, the axial load applied to the first outer ring 35 is the first due to the relative movement of the first outer ring 35 and the first and second cylindrical rollers 36 and 37 in the axial direction. , The second cylindrical rollers 36, 37 and the first inner ring 34 are not loaded. Therefore, the first bearing 31 does not receive the axial load but only the radial load.

On the other side of the outer track 35a in the axial direction (right side in FIG. 3), a large diameter portion 35b having an inner diameter larger than that of the outer track 35a is provided. A second bearing 32 is arranged in the large diameter portion 35b.

The second bearing 32 is made of a deep groove ball bearing. The second bearing 32 is arranged between the first inner ring 34 and the first outer ring 35 of the first bearing 31. The second bearing 32 is arranged at the end of the first bearing 31 on the other side in the axial direction.

The second bearing 32 has a second inner ring 41, a second outer ring 42, and a ball 43.
The second inner ring 41 is formed in an annular shape. The inner peripheral surface of the second inner ring 41 is fitted to the small diameter portion 34e of the first inner ring 34 and fixed to the first inner ring 34. The end surface on one side of the second inner ring 41 in the axial direction is in contact with the stepped surface 34f between the first flange portion 34c and the small diameter portion 34e of the first inner ring 34. Further, the end surface of the second inner ring 41 on the other side in the axial direction is in contact with the retaining ring 40 attached to the small diameter portion 34e. Therefore, the second inner ring 41 is restricted from moving relative to the first inner ring 34 in the axial direction.

The second outer ring 42 is attached to the first outer ring 35. The second outer ring 42 is arranged inside the large diameter portion 35b of the first outer ring 35 in the radial direction. A gap t1 is formed between the second outer ring 42 and the inner peripheral surface of the large diameter portion 35b. The end surface on one side in the axial direction of the second outer ring 42 is in contact with the stepped surface 35c between the outer track 35a of the first outer ring 35 and the large diameter portion 35b.

A retaining ring 38 is attached to the large diameter portion 35b of the first outer ring 35. The retaining ring 38 is in contact with the end surface of the second outer ring 42 on the other side in the axial direction. Therefore, the second outer ring 42 is sandwiched in the axial direction by the stepped surface 35c and the retaining ring 38, and the movement in the axial direction is restricted. Further, since the gap t1 is formed between the second outer ring 42 and the inner peripheral surface of the large diameter portion 35b, the second outer ring 42 is allowed to move in the radial direction.

A seal member 39b is provided between the inner peripheral surface of the large diameter portion 35b and the outer peripheral surface of the small diameter portion 34e of the first inner ring 34 on the other side in the axial direction from the second bearing 32. Further, a seal member 39a is provided between the first inner ring 34 and the first outer ring 35 at one end of the first bearing 31 in the axial direction.

When the drive sprocket 13 and the driven sprocket 14 mesh with the outer peripheral surface of the first outer ring 35 and a radial load and an axial load are applied to the first outer ring 35, the radial load is increased by the presence of the gap t1. No load is applied from the 35 to the second outer ring 42. Therefore, the second bearing 32 is not subjected to a radial load. On the other hand, the axial load applied to the first outer ring 35 is applied from the second outer ring 42 to the ball 43 and the second inner ring 41. That is, the second bearing 32 receives an axial load.

Therefore, in the pressure roller bearing 23 of the present embodiment, the first bearing 31 receives only the radial load, and the second bearing 32 receives only the axial load. Therefore, the contact between the flange portions 34c, 34d of the first inner ring 34 and the end faces of the cylindrical rollers 36, 37 in the first bearing 31 makes it difficult for wear, galling, dents, scratches, etc. to occur, and the resulting first. It is possible to prevent damage to the bearing 31 of 1. In addition, it is possible to prevent rotation failure, lock, track surface roughness, lubrication failure, etc. of the first bearing 31 due to biting of a metal piece generated by galling.

Further, since the second bearing 32 is arranged at the axial end of the first bearing 31, the second bearing 32 can be easily incorporated between the first inner ring 34 and the first outer ring 35. be able to.

[Second Embodiment]
FIG. 4 is a cross-sectional view of the bearing device according to the second embodiment.
In the pressure roller bearing 23 of the present embodiment, the second bearing 32 is not a deep groove ball bearing but a slide bearing.

The second bearing 32 is arranged between the first cylindrical roller 36 and the second cylindrical roller 37. A peripheral groove 34g is formed along the circumferential direction at the center of the flange portion 34d of the first inner ring 34 in the axial direction. Further, in the first outer ring 35, a collar portion 35d is formed between the first cylindrical roller 36 and the second cylindrical roller 37 in the axial direction, and the flange portion 35d is centered in the axial direction in the circumferential direction. A peripheral groove 35 g is formed along the above. The second bearing 32 is arranged in the space S formed between the peripheral groove 34 g of the first inner ring 34 and the peripheral groove 35 g of the first outer ring 35.

The second bearing 32 is made of an elastically deformable synthetic resin such as fluororesin. The second bearing 32 has a rectangular cross section. The second bearing 32 is not continuous in the circumferential direction and is divided into a plurality of bearings 32, each of which is formed in an arc shape following the shapes of the peripheral grooves 34 g and 35 g.

FIG. 5 is an enlarged cross-sectional view showing the second bearing in the second embodiment.
The axial width w1 of the space S is slightly larger than the axial width w2 of the second bearing 32. Therefore, a slight gap is formed between the peripheral grooves 34g and 35g and the second bearing 32 in the axial direction.

On the other hand, the maximum gap t2 between the end faces of the cylindrical rollers 36, 37 arranged on the inner tracks 34a, 34b and the outer track 35a and the flanges 34c, 34d, 35d is the peripheral grooves 34g, 35g and the second. It is larger than the maximum axial clearance with the bearing 32. Therefore, when an axial load is applied to the first outer ring 35, both end faces of the second bearing 32 come into contact with the end faces of the flange portions 34c, 34d, 35d at the same time. At the same time, the peripheral grooves 34g and 35g come into contact with the axial end faces and receive an axial load.

Further, a gap is formed between the inner peripheral surface or the outer peripheral surface of the second bearing 32 and the bottom surfaces of the peripheral grooves 34 g and 35 g. Therefore, the second bearing 32 is not subjected to the radial load applied to the first outer ring 35.
Therefore, also in this embodiment, the same action and effect as in the first embodiment can be obtained.

Further, since the second bearing 32 is elastically deformable, the impact caused by the application of the axial load can be absorbed and mitigated by the elastic deformation in the axial direction.
Since the second bearing 32 is arranged by utilizing the space between the cylindrical rollers 36 and 37 arranged in the double row, it is possible to suppress the increase in size of the bearing device by providing the second bearing 32. Can be done.

An oil passage 32a communicating with the oil passage 34h formed in the first inner ring 34 may be formed inside the second bearing 32.

The present invention is not limited to the above embodiment, and the design can be changed within the scope of the invention described in the claims.
For example, the second bearing 32 in the first embodiment is provided only at one end in the axial direction of the first bearing 31, but may be provided at both ends. In this case, the second bearing 32 may be an angular contact ball bearing.

The second bearing 32 in the first embodiment may be provided at the axial center of the first bearing 31. The second bearing 32 in the second embodiment may be provided at the axial end of the first bearing 31.
The first cylindrical roller 36 and the second cylindrical roller 37 in the first embodiment may have the same axial length. Further, the first cylindrical roller 36 may be shorter than the second cylindrical roller 37.

The second bearing 32 in the second embodiment may be, for example, a spring that expands and contracts in the axial direction.
The first bearing may be in a single row or in a double row of three or more rows.

11: Pallet trolley, 23: Bearing for pressure roller, 31: First bearing, 32: Second bearing, 36: First cylindrical roller, 37: Second cylindrical roller, 43: Ball, t1: Gap

Claims (7)

It consists of an inner ring, an outer ring arranged so as to face the radial outer side of the inner ring, and a cylindrical roller bearing having a plurality of cylindrical rollers arranged between the inner ring and the outer ring, and receives only a radial load. With the first bearing
A bearing device comprising a second bearing arranged between the inner ring and the outer ring and receiving only an axial load. The bearing device is used for a pressurizing roller of a pallet carriage in a sintering facility.
The bearing device according to claim 1, wherein the second bearing is a ball bearing capable of applying an axial load. The bearing device according to claim 1, wherein the second bearing comprises a slide bearing capable of applying an axial load. The bearing device according to claim 3, wherein the second bearing is elastically deformable in the axial direction. The bearing device according to any one of claims 1 to 4, wherein a radial gap is formed between the second bearing and the outer ring or the inner ring. The cylindrical rollers of the first bearing are arranged in multiple rows.
The bearing device according to any one of claims 1 to 5, wherein the second bearing is arranged between the axial directions of the cylindrical rollers in a double row. The bearing device according to any one of claims 1 to 5, wherein the second bearing is arranged at an axial end portion of the first bearing.

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