JP2009063118A - Rolling bearing - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a rolling bearing excellent in workability when fixing a seal. <P>SOLUTION: This rolling bearing comprises a static inner ring 14, a rotating outer ring 16, rolling elements 18 and a seal mechanism for sealing the inside of the bearing. The seal mechanism is structured of a first seal member 22 including an annular part 23b and a second seal member 24 opposite to the first seal member and including an annular part 24c structured of a core metal 24a fixed to the outer ring 16 and an elastic member 24b. The second seal member comprises a seal lip Lp to be brought in slide-contact with the annular part of the first seal member, and the second seal member is fixed by an annular retaining ring 26 to be fitted in a retaining ring groove 16b formed in the outer ring. A surface of the retaining ring on a side outside of the bearing is formed into a tapered shape toward the periphery of the retaining ring. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to a rolling bearing including a stationary wheel maintained in a non-rotating state and a rotating wheel that rotates to face the stationary wheel, particularly for preventing foreign matter from entering the bearing from the outside of the bearing. The present invention relates to an improved sealing mechanism.

Conventionally, various multistage rolling mills are known as rolling equipment for producing steel materials. As an example, the multi-stage rolling mill shown in FIGS. 10 (a) and 10 (b) is provided with a plurality of types of rolling roll groups in the housing 2, and a steel material (not shown) inserted from the insertion port 2a. ) Is rolled to a uniform thickness by a group of rolling rolls while being conveyed along the pass line 2P, and then discharged from the discharge port 2b.
Here, the rolling roll group includes a pair of work rolls 4 for rolling the steel material, a plurality of first intermediate rolls 6 that rotatably support the pair of work rolls 4, and the first intermediate rolls 6 that are rotatable. A plurality of second intermediate rolls 8 to be supported are provided, and each second intermediate roll 8 is rotatably supported by each rolling bearing 12 assembled to a plurality of backing roll shafts 10. Each backing roll shaft 10 is always kept stationary (non-rotating state).

  As shown in FIG. 11, the rolling bearing 12 includes an inner ring (stationary wheel) 14 fitted (fixed) to the backing roll shaft 10 and an outer ring (rotation ring) disposed so as to face the inner ring (stationary wheel) 14. (Rotating wheel) 16, a plurality of rolling elements (cylindrical rollers) 18 assembled in a double row between the inner and outer rings 14, 16, and a cage 20 that holds each rolling element 18 one by one at equal intervals. Yes. Thereby, the rolling bearing 12 has comprised the bearing structure of outer ring | wheel rotation. In the illustrated example, the outer ring 16 has a form having a middle collar, and a lubricating oil or lubricating oil and compressed air are used to lubricate the bearing from a lubricating oil supply hole 54 provided in the inner ring 14. Format.

In such a multistage rolling mill, as shown in FIGS. 10 and 11, the outer ring (rotating ring) 16 of the rolling bearing 12 is in pressure contact with the plurality of second intermediate rolls 8, and the second intermediate roll 8 And is positioned so as to be rotatable. In this case, the pressure of each outer ring 16 acts on the pair of work rolls 4 from the second intermediate roll 8 through the first intermediate roll 6, thereby preventing the work roll 4 from being bent. Thereby, the steel material conveyed along the pass line 2 </ b> P is rolled to a uniform thickness by the pair of work rolls 4.
In addition, as a material of the inner / outer rings 14, 16 and the rolling elements 18, for example, a steel material such as alloy steel can be used.

The rolling bearing 12 is provided with a sealing mechanism for sealing the inside of the bearing from the outside of the bearing in order to prevent intrusion of foreign matters (for example, dust, rolling oil) from the outside of the bearing to the inside of the bearing.
Further, in this case, in order to support the flow of the lubricating oil supplied into the bearing, compressed air is sent from a lubricating oil supply source (not shown) to the lubricating oil supply hole 54, and the compressed air, together with the lubricating oil, After being supplied to the inside of the bearing through the lubricating oil path and the lubricating oil supply hole 54, the sealing mechanism is reached through between the double row rolling elements 18.

"Prior art 1"
FIG. 11 shows an example of the sealing mechanism, and the sealing mechanism is provided between the inner and outer rings 14 and 16 on both sides of the double row rolling elements 18 (Non-Patent Document 1).

The sealing mechanism shown in FIG. 11 has an annular shield 22 in which an inner diameter 22e is fixed (press-fitted) to an inner ring (stationary ring) 14 and an outer diameter 22t is positioned in a non-contact state with respect to an outer ring (rotating ring) 16. And an annular seal 24 disposed inside the bearing relative to the shield 22.
Here, the seal 24 has an outer diameter 24 e fixed to the outer ring (rotating ring) 16 and an inner diameter 24 t extending toward the inner ring (stationary ring) 14, and an extending end (seal lip) extends from the inner diameter 24 t to the shield 22. It is inclined in the direction and positioned so as to be in sliding contact with the shield 22.

  In this case, the seal 24 is formed by covering the core metal 24a with the rubber material 24b, and a rubber lip Lp protruding in a substantially V shape toward the shield 22 is integrally formed on the inner diameter 24t thereof. The lip Lp is always in sliding contact with the shield 22. The outer diameter 24 e of the seal 24 is fitted and fixed to the outer ring (rotating ring) 16 by an annular retaining ring 26.

However, the sealing mechanism (prior art 1) disclosed in Non-Patent Document 1 shown in FIG. 11 has the following problems.
That is, in Non-Patent Document 1, the outer ring 16 is provided with a seal 24, and the outer diameter 24e of the seal 24 is such that the annular retaining ring 26 is pressed against the outer diameter 24e from the thrust direction. It is fixed. In this case, an annular retaining ring groove 16b continuous in the circumferential direction is formed on the inner circumferential surface of the outer ring (rotating ring 16), and a retaining ring 26 is fitted into the retaining ring groove 16b and fixed.

Specifically, in the present embodiment, the outer diameter 24e of the seal 24 is applied to a step portion 16c formed on the inner peripheral surface of the outer ring (rotating ring 16), and positioning in the bearing inner direction is performed. The outer ring (rotating ring 16) is positioned in the bearing external direction by an annular retaining ring 26 fitted on the bearing outer side than the seal 24 on the inner peripheral surface of the outer ring (rotating ring 16).
At this time, since the retaining ring 26 comes into contact (surface contact) with the surface facing the seal 24 in a wide area, it is necessary to apply a large force in the thrust direction when the retaining ring 26 is fitted to or removed from the retaining groove 16b. Yes, workability may be impaired.

Product catalog (JTEKT Corporation product catalog Multi-stage rolling mill Cylindrical roller bearing for backup roll CAT.NO.246 P5 Figure 4)

  The present invention has been made to solve such a problem, and an object of the present invention is to provide a rolling bearing with good workability when the seal is fixed.

In order to achieve such an object, the first invention rolls between a stationary wheel maintained in a non-rotating state, a rotating wheel rotating opposite to the stationary wheel, and the stationary wheel and the rotating wheel. A plurality of rolling elements incorporated freely, and a sealing mechanism for sealing the inside of the bearing defined between the stationary ring and the rotating ring from the outside of the bearing, and the sealing mechanism is one of the rotating ring and the stationary ring. A first seal member including an annular portion made of an annular core, and fixed to the other of the rotating wheel and the stationary wheel, and an annular core, A second seal member that includes an annular portion that includes an elastic member that covers the core metal, and the annular portion is disposed so as to face the annular portion of the first seal member in the axial direction. The second seal member is inclined from the predetermined region of the elastic member constituting the annular portion toward the annular portion of the first seal member. An annular seal lip that extends integrally in the shape of the first seal member and forms a contact seal region in sliding contact with the annular portion of the first seal member, of the first seal member and the second seal member, Any one of the seal members is a rolling bearing having a structure fixed by an annular retaining ring fitted in a circumferential groove formed in a rotating wheel or a stationary wheel provided with the sealing member, and the retaining ring One or both of the bearing inner side and the bearing outer side are tapered toward the outer periphery of the retaining ring.
According to the first invention, since the retaining ring is formed in a tapered shape toward the outer periphery, when the retaining ring is fitted into the circumferential groove, the outer peripheral side whose thickness is reduced in the tapered shape of the retaining ring is the circumferential groove. It is not necessary to apply a large force in the thrust direction, and workability is improved.
In addition, workability is improved even if the outer bearing portion of the groove portion is tapered in the retaining ring of the outer ring.

In a second aspect based on the first aspect, the stationary ring is configured as an inner ring disposed opposite to the inner side of the rotating ring, and the rotating ring is configured as an outer ring disposed opposite to the outer side of the inner ring. This is a rolling bearing characterized by this.
According to the second aspect of the invention, it is possible to configure an outer ring rotary rolling bearing in which the inner ring does not rotate and the outer ring rotates.

According to a third aspect of the present invention, there is provided a rolling bearing characterized in that in the first aspect of the invention, the inside of the bearing is lubricated using lubricating oil or lubricating oil and compressed air.
According to the third aspect of the invention, the inside of the bearing is in a lubricating oil supply state. However, since the inner ring and the sealing mechanism are not provided with a recovery hole or an exhaust hole, the load resistance is not lowered, and the seal lip is not provided. There are no restrictions.

4th invention is the rolling bearing used for the multistage rolling mill which rolls steel materials in 1st invention, Comprising: A multistage rolling mill is provided with the rolling roller group for rolling steel materials. The rolling bearing is a rolling bearing characterized by being assembled to a backing roll shaft of a group of rolling rollers.
According to the fourth invention, it is possible to provide a sealing mechanism suitable for the bearing structure of the backing roll shaft in a simple and inexpensive manner.

  According to the present invention, it is possible to provide a rolling bearing with good workability when the seal is fixed.

Hereinafter, a rolling bearing according to an embodiment of the present invention will be described with reference to the accompanying drawings.
1 shows the first embodiment, FIG. 2 shows the second embodiment, FIG. 3 shows the third embodiment, FIG. 7 shows the fourth embodiment, FIG. 8 shows the fifth embodiment, and FIG.
Each of the embodiments is an improvement of the sealing mechanism of the rolling bearing 12 (FIG. 10) used in the multi-stage rolling mill shown in FIG. 10, and therefore only the improved part will be described below. In this case, with respect to the same configuration as the rolling bearing 12 disclosed in FIG. 10 described above, the same reference numerals as those used in the configuration are attached to the drawings used in the present embodiment to explain the configuration. Omitted. That is, in this embodiment, for example, in order to support the flow of the lubricating oil supplied into the bearing, compressed air is sent together with the lubricating oil from a lubricating oil supply source (not shown) to the lubricating oil supply hole 54, and the compression The air employs a lubrication configuration in which the air is supplied together with the lubricating oil through the lubricating oil path and the lubricating oil supply hole 54 and then reaches the sealing mechanism through the two rows of rolling elements 18.
Of course, the case where only the lubricating oil is supplied without compressed air is also within the scope of the present invention.
In the rolling bearing of the present embodiment, the lubricating oil recovery hole is not provided in the inner ring 14, and the compressed air discharge hole is not provided in the sealing mechanism.
Furthermore, in this embodiment, as an application example of the rolling bearing of the present invention, the multi-stage rolling mill shown in FIG. 9 is used as described above. However, the rolling bearing of the present invention is limited to this multi-stage rolling mill. However, the design can be changed within the scope of the present invention. In the present embodiment, the inner ring 14 is described as a stationary wheel and the outer ring 16 is a rotating wheel. However, it is within the scope of the present invention to apply the inner ring 14 as a rotating wheel and the outer ring 16 as a stationary wheel.

  The sealing mechanism shown in FIG. 1 includes a first seal member 22 fixed to the inner ring 14 as a stationary ring and a second seal member 24 fixed to the outer ring 16 as a rotating ring. It is configured. 1B is an enlarged view of the sealing mechanism disposed on the right side in FIG. 1A, the sealing mechanism disposed on the left side in FIG. It is the same structure except being comprised symmetrically.

  The first seal member 22 includes a shield 22 formed of an annular cored bar 23 that is positioned in a non-contact state with respect to the outer ring (rotating ring) 16, and the shield 22 has an inner diameter 22 e of an inner ring (stationary ring) 14. Are fitted together. Specifically, the shield 22 includes a first cylindrical portion 23a that is fixed (press-fit), and an annular portion (disc portion) that extends radially from the first cylindrical portion 23a toward the outer ring 16. ) 23b and a second cylindrical portion 23c extending in a non-contact manner from the outer ring 16 from the outer ring 16 side of the disk portion 23b, and forms a substantially inverted S-shape in FIG. 1 (b). is doing.

  The second seal member 24 is configured by covering an annular cored bar 24 a positioned on the bearing inner side with respect to the shield 22 with an elastic member (for example, rubber material) 24 b, and an outer ring (rotating ring) 16. An outer diameter 24e fixed to the inner ring (stationary ring) 14 from the outer diameter 24e toward the inner ring (stationary ring) 14 in the inner diameter direction, and an inner diameter 24t of the annular section 24c. Yes. The core member 24a is covered with an elastic member 24b except for the surface portion 24d on the bearing outer side.

The inner diameter 24t side of the elastic member (for example, rubber material) 24b protrudes slightly in the direction of the inner ring 14 from the inner diameter of the cored bar 24a, and is provided in non-contact with the inner ring 14. The leading end (lip) Lp extends.
The lip Lp protrudes in a substantially V shape inclined outward toward the bearing inner surface 23 d of the annular portion 23 b of the first seal member (shield) 22, and is integrated with the inner diameter 24 t of the seal 24. It is formed and forms a sliding contact seal that is always in sliding contact with the shield 22 (also referred to as a V-type seal or a Y-type seal from the shape of the seal). As a result, the lip Lp is in sliding contact with the first seal member 22 fixed to the inner ring 14 to form a contact seal region.
The size of the lip Lp, the arrangement position, or the size of the contact area is not particularly limited and can be changed within the scope of the present invention according to the specification. For example, it is possible to make the lip Lp large and have a long structure with low rigidity.

  The outer diameter 24e is applied to a step portion 16c formed on the inner peripheral surface of the outer ring (rotating wheel 16) to be positioned in the bearing inner direction and to seal the inner peripheral surface of the outer ring (rotating wheel 16). It is fixed by positioning in the bearing external direction by a retaining ring 26 having a rectangular cross section and an annular shape, which is fitted to the bearing outer side than 24.

As shown in FIG. 1B, the retaining ring 26 has an outer diameter slightly smaller than the inner periphery of the retaining ring groove 16b. Further, the inner diameter is formed slightly larger than the inner diameter of the elastic member 24b on the outer side 24f of the bearing covering the outer diameter 24e of the seal 24, so that the inner diameter side of the retaining ring 26 is set on the outer side 24f of the bearing. It becomes possible to oppose the elastic member 24b.
Furthermore, a tapered inclined surface 26a is formed on the outer peripheral side of the retaining ring 26 in the bearing outer direction toward the outer periphery. As a result, the retaining ring 26 is set such that the inner diameter side thickness D1 is set to be slightly smaller than the width of the retaining ring groove 16b in the bearing axial direction, and the outer diameter side thickness D2 is set to the inner diameter side. It is set smaller than the thickness D1.
Note that the angle and size of the tapered inclined surface 26a can be freely set according to the usage environment of the rolling bearing and the convenience of work, and are not particularly limited here. In addition, the surface shape of the inclined surface 26a is formed in a surface shape in this embodiment, but is not limited to this, and the outer diameter side thickness D2 is set smaller than the inner diameter side thickness D1. If it is, it does not need to be formed in a planar shape. For example, it may be formed in a curved shape.

  By being configured as in the present embodiment, the sealing mechanism improves the workability particularly when the retaining ring 26 is fitted to the retaining ring groove 16b or removed in order to install the seal 24. That is, when fitting the retaining ring 26 into the retaining ring groove 16b, first, the retaining ring 26 is bent and the outer diameter side of the retaining ring 26 is fitted into the retaining ring groove 16b. At this time, since the tapered inclined surface 26a is formed on the outer peripheral side of the retaining ring 26 in the bearing outer direction toward the outer periphery, the thickness D2 on the outer peripheral side of the retaining ring 26 is changed to the thickness D1 on the inner peripheral side. The outer diameter of the retaining ring 26 is easy to enter the retaining ring groove 16 and the workability is good. Further, when the retaining ring 26 returns to the original annular shape from the bent shape, the tapered inclined surface 26a and the inner wall surface 16d on the bearing outer side of the retaining ring groove 16b come into contact with each other. Since a force that is pushed in the bearing inner direction (thrust direction) acts on 26, this makes it easy to press the elastic member 24b of the seal 24 from the thrust direction, and the retaining ring 26 easily engages with the retaining ring groove 16b. Fitted together.

Further, when the retaining ring 26 is removed from the retaining ring groove 16b, the retaining ring 26 is pulled out from the retaining ring groove 16b while being bent. When the groove 16b is pulled out, the outer peripheral side of the retaining ring 26 is dropped by the tapered inclined surface 26a formed toward the outer periphery on the outer peripheral side of the retaining ring 26 in the bearing outer direction (outer peripheral side). Therefore, the retaining ring 26 can be easily extracted from the retaining ring groove 16b, and the workability is improved.
In this embodiment, the tapered inclined surface 26a is provided on only one surface of the retaining ring 26. However, the present invention is not limited to this, and the tapered inclined surface 26a is provided on both surfaces of the retaining ring 26. It may be done. Even in this case, the same effect as in the present embodiment can be obtained.

Further, by adopting such a sealing mechanism, the bearing internal pressure is the sum of the rigidity of the seal lip Lp and the bearing external pressure in a type in which lubrication is performed using lubricating oil or lubricating oil and compressed air as in this embodiment. If higher, the seal lip Lp is opened by the bearing internal pressure, and the lubricating oil and air are discharged. Accordingly, since it is possible to create a flow of lubricating oil supplied into the bearing without providing a recovery hole or an exhaust hole in the inner ring 14 or the sealing mechanism, poor lubrication in the bearing and in the seal lip Lp region is prevented. A lubrication system is stably formed. In addition, since no exhaust hole is provided, it is possible to prevent foreign matter and rolling oil from entering through the exhaust hole, which can contribute to prevention of early seizure and early damage of the bearing.
According to the present embodiment, since the seal lip Lp is integrally provided in a predetermined region of the elastic member 24b integrally forming the second seal member 24, the process of incorporating the sealing mechanism is simple, and the bearing It is possible to save the space in the area where the sealing mechanism is disposed.

  Further, according to the present embodiment, the inside of the bearing is in a lubricating oil supply state. However, since the inner ring 14 and the sealing mechanism are not provided with a recovery hole or an exhaust hole, the load resistance is not deteriorated and the seal is sealed. There is no restriction of the lip Lp. That is, the seal lip Lp may be contacted (slidably contacted) as long as it is the surface portion 23d on the bearing inner side of the annular portion 23b of the core metal of the first seal member 22, and the adjustment of the lip opening pressure of the seal Is easy.

The sealing mechanism of the present embodiment shown in FIG. 2 is different from the first embodiment in that a tapered inclined surface 26 a is provided on the bearing inner side of the retaining ring 26. Since the other configuration is the same as that of the first embodiment, the description will focus on the retaining ring 26, which is a characteristic part of the present embodiment, and the surrounding configuration, and the other description will be omitted.
In this embodiment, as shown in FIG. 2A, the outer diameter is formed to be slightly smaller than the inner circumference of the retaining ring groove 16b. Further, the inner diameter is formed slightly larger than the inner diameter of the elastic member 24b on the outer side 24f of the bearing covering the outer diameter 24e of the seal 24, so that the inner diameter side of the retaining ring 26 is set on the outer side 24f of the bearing. It becomes possible to oppose the elastic member 24b.
Furthermore, a tapered inclined surface 26a is formed on the outer peripheral side of the retaining ring 26 in the bearing inner direction toward the outer periphery. Thereby, the thickness of the retaining ring 26 is set to be smaller than the width in the bearing axial direction of the retaining ring groove 16b, and the outer diameter D2 is set to be smaller than the inner diameter D1. .
Note that the angle and size of the tapered inclined surface 26a can be freely set according to the usage environment of the rolling bearing and the convenience of work, and are not particularly limited here. In addition, the surface shape of the inclined surface 26a is formed in a surface shape in this embodiment, but is not limited to this, and the outer diameter side thickness D2 is set smaller than the inner diameter side thickness D1. If it is, it does not need to be formed in a planar shape. For example, it may be formed in a curved shape.

Further, in this embodiment, the retaining ring groove 16b has a width dimension (axial dimension) larger than the axial dimension of the retaining ring 26, and the bearing outer side 24f of the elastic member 24b of the seal 24. Are integrally extended from the elastic member 24b with a predetermined dimension in the axial direction, and a projecting portion 24g having a convex cross section that is continuous in the circumferential direction is formed in an annular shape on one circumference.
In this case, therefore, when the retaining ring 26 is fitted into the retaining ring groove 16b, a predetermined interval (gap) 16e is generated between the opposing surfaces of the retaining ring 26 and the seal 24.
The projecting portion 24g of the seal 24 is provided for the purpose of eliminating the clearance 16e. For this reason, a larger dimension than the clearance 16e is set as the predetermined dimension from which the projecting portion 24g projects. The protruding portion 24g is formed in an annular shape that is continuous in the circumferential direction, and has a tapered shape toward the protruding end 24h.
Thus, when the seal 24 is positioned and fixed, the retaining ring 26 fitted in the retaining ring groove 16b pushes the seal 24 from the outside of the bearing against the projecting end 24h of the projecting part 24g from the thrust direction in the thrust direction. Hit it.

By being configured as in the present embodiment, the sealing mechanism particularly improves the workability when fitting the retaining ring 26 to the retaining ring groove 16b or removing it in order to install the seal 22. That is, when fitting the retaining ring 26 into the retaining ring groove 16b, first, the retaining ring 26 is bent and the outer diameter side of the retaining ring 26 is fitted into the retaining ring groove 16b. At this time, since the tapered inclined surface 26a is formed on the outer peripheral side of the retaining ring 26 in the bearing inner direction toward the outer periphery, the thickness D2 on the outer peripheral side of the retaining ring 26 is changed to the thickness D1 on the inner peripheral side. The outer diameter of the retaining ring 26 is easy to enter the retaining ring groove 16 and the workability is good. Further, when the retaining ring 26 returns from the bent shape to the original annular shape, the tapered inclined surface 26a and the protruding portion 24g of the seal 24 come into contact with each other, so that the seal 24 is supported by the retaining ring 26. Since a force for pushing in the internal direction (thrust direction) is generated, this makes it easy to press the elastic member 24b of the seal 24 from the thrust direction, and the retaining ring 26 is easily fitted into the retaining ring groove 16b.
Furthermore, in the sealing mechanism according to the present embodiment, the seal 24 can be stably installed. Specifically, since the retaining ring 26 is pressed against the projecting end 24h of the projecting portion 24g from the outside of the bearing against the outer diameter 24e of the seal 24 from the thrust direction, the seal 24 does not rattle, Positioning and fixing are stable. Thereby, since the distance between the seal 24 and the shield 22 does not change, there is no variation in the tightening force of the seal lip Lp.
Further, since the retaining ring 26 and the seal 24 are in contact with each other only at the projecting end 24h of the projecting part 24g, the projecting part 24g is easily bent when the retaining ring 26 is fitted to or removed from the retaining groove 16b. This eliminates the need to apply a large force to the work and improves workability.

Further, as shown in FIG. 2B, the tapered inclined surface 26a of the retaining ring 26 gradually decreases from the inner peripheral side thickness D1 to the outer peripheral side thickness D2 of the retaining ring 26 in the bearing inner direction. Thus, it may be formed over the entire surface.
In this case, the inclination angle of the inclined surface 26a becomes gentler than the inclination angle of the inclined surface 26a of the present embodiment described above. Therefore, when the retaining ring 26 returns to the original annular shape from the bent shape, the seal 24 is generated in the bearing inner direction (thrust) generated by the contact between the tapered inclined surface 26a and the protruding portion 24g of the seal 24. ), The elastic member 24b of the seal 24 can be more easily pressed from the thrust direction, and the retaining ring 26 is easier. Are fitted into the retaining ring groove 16b to improve workability.

In the present embodiment, the case where the annular projecting portion 24g of the seal 24 is continuously formed in the circumferential direction and formed in one annular shape is described. However, the present invention is not limited to this, and the projecting portion is not limited thereto. An annular projecting portion may be further formed on the inner peripheral side or the outer peripheral side of the portion 24g to form a projecting portion having two or more circumferences. In this case, the retaining ring 26 fitted in the retaining ring groove 16b presses the projecting portion 24g and each projecting end 24h of the additionally formed projecting portion against the seal 24 from the outside of the bearing in the thrust direction. It is done. Thereby, the positioning and fixing of the seal 24 becomes more reliable. Further, the protrusion 24g may not be continuous in an annular shape. For example, it may be provided intermittently in an annular shape, or may be provided with a conical protrusion 24g.
Even in this case, since the retaining ring 26 is in contact with each projecting end 24h of the projecting portion additionally formed with the projecting portion 24g, a large force is applied in the thrust direction when each projecting end 24h is bent. It is not necessary and workability is not impaired.

Further, in the present embodiment, the case where the annular projecting portion 24g of the seal 24 is formed on the bearing outer side 24f of the outer diameter 24e of the seal 24 is not limited to this, but the projecting portion 24g is not limited thereto. Is the outer diameter 24 of the seal 24 instead of the protruding portion 24g formed on the bearing outer side 24f, and is a surface applied to the step portion 16c formed on the inner peripheral surface of the outer ring (rotating ring 16). It may be formed. Or the protrusion part 24g may be formed in both the bearing outer side 24f and the surface applied to the step part 16c. Even in these cases, it is possible to obtain the same effect as when the protrusion 24g is formed on the bearing outer side 24f.
Further, the protruding portion 24g may be formed on the retaining ring 26 instead of the protruding portion 24g formed on the seal 24. In this case, the protruding portion 24g only needs to be formed at least in a portion where the seal 24 of the retaining ring 26 is pressed from the thrust direction.
Furthermore, in the present embodiment, the case where the retaining ring 26 is formed in an annular shape has been described. However, the present invention is not limited to this, and the retaining ring 26 can be attached to and detached from the retaining ring groove 16b. If it exists, it does not necessarily have to be annular.

  In the present embodiment, the configuration in which the retaining ring groove 16b has a larger width dimension than the axial dimension of the retaining ring 26 and the seal 24 is provided with the protrusion 24g has been described. However, the present invention is not limited to this, and like the first embodiment, the retaining ring groove 16b may be formed in the retaining ring 26 according to the thickness, and the seal 24 is not provided with the protruding portion 24g. Even if it is a structure, the effect similar to a present Example is acquired.

Moreover, in Example 1 and Example 2 mentioned above, although the tapered inclined surface 26a is formed in the retaining ring 26, it is not restricted to this, The inclined surface 26a may be formed in the retaining ring groove 16b. .
In the example shown in FIG. 4, a seal 24 and a shield 22 similar to those in the first embodiment (FIG. 1) are provided, and a retaining ring 26 having no inclined surface is provided. Further, a tapered inclined surface 200 is formed on the inner diameter side of the inner wall surface 16d on the bearing outer side of the retaining ring groove 16b in which the retaining ring 26 is fitted.
4A shows the case where the inner wall surface 16d of the retaining ring groove 16b is in contact with a part of the retaining ring 26, and FIG. 4B shows the case where the inner wall surface 16d of the retaining ring groove 16b is stopped. The case where it does not contact the ring | wheel 26 is shown.
Even when formed in this way, the same effects as those of the first embodiment can be obtained.

Further, the example shown in FIG. 5 includes the seal 24 and the shield 22 similar to those of the second embodiment (FIG. 2), and the retaining ring 26 having no inclined surface. Further, a tapered inclined surface 200 is formed on the entire inner wall surface 16d on the bearing outer side of the retaining ring groove 16b in which the retaining ring 26 is fitted.
5A shows the case where the inner wall surface 16d of the retaining ring groove 16b is in contact with a part of the retaining ring 26, and FIG. 5B shows the case where the inner wall surface 16d of the retaining ring groove 16b is stopped. The case where it does not contact the ring | wheel 26 is shown.
Even when formed in this way, the same effects as those of the second embodiment described above can be obtained.

  The sealing mechanism of the present embodiment shown in FIG. 3 includes a first seal member 80 that is fixed to the outer ring 16 as a rotating wheel and a second seal member 90 that is fixed to the inner ring 14 as a stationary ring. It consists of and. 2 is an enlarged view of another example of the sealing mechanism disposed on the right side in FIG. 1A, the sealing mechanism disposed on the left side in FIG. The configuration is the same except that the configuration is symmetrical.

  The first seal member 80 has a continuous outer diameter 82b together with an annular cored bar 82 provided in non-contact with the inner ring 14 and the entire region of the bearing inner side surface 82a of the cored bar 82. A shield including an annular portion 87 composed of an elastic member 84 to be covered is press-fitted by fitting the outer diameter 82b side to the inner diameter surface of the outer ring 16, and is disposed inward in the axial direction of the bearing.

An elastic member (for example, a rubber material) 84 protrudes slightly toward the inner ring 14 from the inner diameter of the cored bar 82 and is not in contact with the inner ring 14 on the outer diameter 82 b of the shield (first seal member) 80. ing. Therefore, the surface portion 82c on the bearing outer side of the cored bar 82 is not covered with the elastic member 84 and the cored bar 82 is exposed. Further, the outer side of the bearing on the outer diameter 82b side of the elastic member 84 has a projecting portion 84g having a convex cross section that is integrally extended from the elastic member 84 with a predetermined dimension in the axial direction.
Further, in this embodiment, the outer diameter 82b of the shield 80 is applied to the step portion 16c formed on the inner peripheral surface of the outer ring (rotating ring 16) to be positioned in the bearing inner direction, and the outer ring ( The rotating ring 16) is fixed by a retaining ring 26 having a rectangular cross section and an annular shape, which is fitted to the outside of the bearing with respect to the shield 80 on the inner peripheral surface.

The projecting portion 84g extends in the axial direction with a dimension larger than the clearance 16e between the shield 80 and the retaining ring 26, and is formed in a tapered shape toward the projecting end 84h. Is formed.
As a result, when the shield 80 is positioned and fixed, the retaining ring 26 fitted in the retaining ring groove 16b pushes against the projecting end 84h of the projecting portion 84g from the outside of the bearing to the shield 80 from the thrust direction. Hit it.

The second seal member 90 is a cylindrical portion 92 a fitted to the outer diameter surface of the inner ring 14, and a circular plate that extends radially from the cylindrical portion 92 a toward the outer ring 16 and is not in contact with the outer ring 16. A core metal 92 having a substantially L-shaped cross-sectional view composed of a portion 92b, an entire area of the outer diameter surface 92c of the cylindrical portion 92a of the core metal 92, and an entire area of the surface portion 92d on the bearing inward side of the disk portion 92b. The annular member 96 that is formed by the elastic member 94 that continuously covers the outer diameter 92e and the elastic member 94 that covers the surface 92d on the inner side of the bearing of the disk member 92b are integrally extended. The contact seal is constituted by a seal lip 98 that is in sliding contact with the first seal member 80 (also referred to as a V-type seal or a Y-type seal from the shape of the seal).
Then, the inner diameter surface of the cylindrical portion 92 a is fitted into the outer diameter surface of the inner ring 14 and press-fitted, and is disposed outward in the axial direction of the bearing so as to face the annular portion 87 of the first seal member 80. .

The seal lip 98 is a bearing of the cored bar 82 in the first seal member 80 from a predetermined region of the elastic member 94 that covers the inner surface 92d of the disk portion 92b of the elastic member 94 constituting the annular portion 96. The first seal member 80 is integrally extended in an inclined shape (inclined outward) toward the outer surface portion 82c, and is slidably contacted with the rotation of the outer ring 16, thereby forming a contact seal region. An annular seal lip.
Specifically, according to the present embodiment, from the substantially central position in the radial direction between the inner diameter and the outer diameter of the disk portion 92b, the wall portion is thinner than the branch portion 98a through the thick cylindrical branch portion 98a. An overall conical shape having a substantially V-shaped cross-sectional view inclined toward the outer diameter 82b direction which is the fixed side of the first seal member 80 (the large diameter D3 side is opposed to the first seal member 80 direction) The seal lip has a shape that is
The size of the seal lip 98, the position of the seal lip 98, and the size of the contact area are not particularly limited and can be changed within the scope of the present invention according to specifications. For example, the seal lip 98 can be made large to have a long structure with low rigidity.

By being configured as in the present embodiment, the sealing mechanism can obtain the same effects as those of the first embodiment described above, and can also prevent intrusion of foreign matter, rolling oil, and the like from the outside of the bearing.
In addition, with such a sealing mechanism, the bearing internal pressure is the sum of the rigidity of the seal lip 98 and the bearing external pressure in a type in which lubrication is performed using lubricating oil or lubricating oil and compressed air as in this embodiment. If higher, the seal lip 98 is opened by the bearing internal pressure, and the lubricating oil and air are discharged. Accordingly, it is possible to create a flow of lubricating oil supplied into the bearing without providing a recovery hole or an exhaust hole in the inner ring 14 or the sealing mechanism, thereby preventing poor lubrication inside the bearing and in the seal lip 98 region. . Further, since no exhaust hole is provided, it is possible to prevent foreign matter or rolling oil from entering through the exhaust hole, which can contribute to prevention of early damage to the bearing.
According to the present embodiment, the second seal member 90 disposed on the inner ring 14 is provided with the seal lip 98 that slides on the first seal member 80 that rotates together with the outer ring 16 to form a seal region of contact. Therefore, there is no problem that the sealing lip forming the contact sealing region as in the prior art is opened by the centrifugal force and the sealing performance is deteriorated.
In addition, since the seal lip 98 is integrally provided in a predetermined region of the elastic member 94 integrally forming the second seal member 90, the process of incorporating the seal mechanism is simple, and the seal mechanism inside the bearing is It is possible to save the installation area.
Further, according to the present embodiment, the inside of the bearing is in a lubricating oil supply state. However, since the inner ring 14 and the sealing mechanism are not provided with a recovery hole or an exhaust hole, the load resistance is not deteriorated and the seal is sealed. There are no restrictions on the lip 98. That is, the seal lip 98 may be in contact (sliding contact) as long as it is a surface portion 82c on the bearing outer side of the metal core 82 of the first seal member 80, and the adjustment of the lip opening pressure of the seal is easy. .

In the third embodiment, the tapered inclined surface 26a is formed on the retaining ring 26. However, the present invention is not limited to this, and the inclined surface 26a may be formed in the retaining ring groove 16b.
In the example shown in FIG. 6, the same seal 24 and shield 22 as those of the third embodiment are provided, and a retaining ring 26 having no inclined surface is provided. Further, a tapered inclined surface 200 is formed on the inner diameter side of the inner wall surface 16d on the bearing outer side of the retaining ring groove 16b in which the retaining ring 26 is fitted.
6A shows the case where the inner wall surface 16d of the retaining ring groove 16b is in contact with a part of the retaining ring 26, and FIG. 6B shows the case where the inner wall surface 16d of the retaining ring groove 16b is stopped. The case where it does not contact the ring | wheel 26 is shown.
Even if it is formed in this way, the same effect as in Example 3 can be obtained.

FIG. 7 is a schematic sectional view showing a part of the rolling bearing according to the third embodiment of the present invention.
This embodiment is an embodiment in which a floating ring 100 is provided between double-row cylindrical rollers, and the sealing mechanism of the present invention is applied to the sealing mechanism.
The floating ring 100 cooperates with the inner ring collars 14a and 14a and the outer ring collar 16a to restrict the axial movement of the rolling elements (cylindrical rollers) 18 in each row and to prevent the rolling elements (cylindrical rollers) 18 from skewing. This is a well-known configuration to prevent.
Since other configurations and operational effects are the same as those of the first embodiment, description thereof is omitted.

FIG. 8 is a schematic sectional view showing a part of the rolling bearing according to the fourth embodiment of the present invention.
In the present embodiment, the sealing mechanism of the present invention is applied to an example in which the outer collar 14a of the inner ring 14 is a separate part.
8A shows a type in which the lubricating oil supply hole 54 is provided in the inner ring, and FIG. 8B shows a spacer 102 between the inner rings 14 and 14 and a floating ring between the rolling elements (cylindrical rollers) 18 and 18. 1 is an embodiment including 100.
Since other configurations and operational effects are the same as those of the first embodiment, description thereof is omitted.

FIG. 9 is a schematic sectional view showing a part of the rolling bearing according to the fifth embodiment of the present invention.
The present embodiment is an embodiment in which the sealing mechanism of the present invention is applied to a double-row tapered roller bearing incorporating a double-row tapered roller as the rolling element 18.
Since other configurations and operational effects are the same as those of the first embodiment, description thereof is omitted.
"Modification 1"

In each of the above-described embodiments, the seal lip Lp (98) has a single configuration. For example, the seal lip Lp (98) includes a plurality of lips that come into contact with the surface portion 23d on the bearing inner side of the core metal in the first seal member 22. Alternatively, for example, even if the first seal member 80 includes a plurality of lips that come into contact with the surface portion 82c on the bearing outer side of the core metal 82, the same effects as those of the first embodiment described above can be obtained. And are within the scope of the present invention. Further, even if the plurality of lips are branched from the seal lip Lp (98) of the present embodiment, the plurality of lips are protruded from a predetermined region of the elastic member 94 separately from the seal lip 98 of the present embodiment. Although there may be, care must be taken so that the torque is not too high.
"Modification 2"

In Examples 1 to 3 shown in FIGS. 1 to 9 described above, “cylindrical rollers” are illustrated as the rolling elements 18, and in Example 5 shown in FIG. 8, “conical rollers” are shown as the rolling elements 18. However, the same effect can be obtained even if other rolling element forms such as “balls” are applied. Further, in each of the embodiments described above, the bearing structure is provided with the rolling elements 18 in two rows in the axial direction. However, the same effect can be obtained by using one row or three or more rows in the axial direction.
“Modification 3”

Foreign materials such as metal chips, shavings, burrs, and wear powder may be mixed in the bearing lubricant, and these foreign materials may damage the races and rolling elements, resulting in a significant decrease in bearing life. You may be invited. The inner and outer rings 14 and 16 and the rolling elements 18 can be formed of a steel material such as alloy steel as in the conventional case. However, since the inner ring 14 does not rotate with the shaft 10, The load applied to the inner ring 14 is always applied in the same phase with respect to the applied radial load. Therefore, the inner ring 14 has a fatigue life earlier than the outer ring 16 and the rolling elements 18. That is, there is also a problem that the life is likely to be shortened due to damage caused by foreign matter.
Therefore, the inner ring as a stationary ring is preferably configured as follows.
That is, for example, for example, an alloy mainly containing carbon (C); 0.1 to 1.2% by weight, chromium (Cr); 1 to 3% by weight, and further containing 2.0% by weight or less of molybdenum (Mo). Made of steel, carburized or carbonitrided to form a surface layer (also called rolling surface layer), the amount of retained austenite (γR vol%) of the surface layer is 20 to 45 vol%, fine carbide or carbonitride The average particle size is 2.3 μm or less.
Moreover, it is preferable that the average particle diameter of a fine carbide | carbonized_material or a carbonitride shall be 0.5-1.5 micrometers, for example.
The surface hardness (Hv) of the surface layer is in the range of −4.7 × (γR vol%) + 920 ≦ Hv ≦ −4.7 × (γR vol%) + 1020 with respect to the amount of retained austenite (γR vol%). Is preferred.
Further, the molybdenum (Mo) content is preferably 1/3 or more of the chromium (Cr) content.
By configuring the inner ring 14 in this way, an effect that the life of the inner ring 14 can be extended is obtained.
“Modification 4”

Moreover, in the said Example 1, the annular part (disk part) 23b of the metal core 23 in the 1st sealing member 22 is made into a flat shape, and in the said Example 2, the metal core 92 in the 2nd sealing member 90 is used. Although the disk portion 92b has a flat shape, a concave portion and a convex portion (not shown) that are continuous in the circumferential direction can be configured in a side view wave shape by being arranged in concentric circles having the same axial center. And within the scope of the present invention. By comprising in this way, the intensity | strength of a metal core improves and it can prevent the deformation | transformation at the time of press-fitting in the inner ring | wheel 14 and fitting. Accordingly, the seal lip Lp (98) hits the disc portion 23b (92b) too much due to the deformation of the core metal, or the seal lip Lp (98) does not hit the disc portion 23b (92b) and the contact seal area is The problem of not being formed can be prevented. As a result, the bearing can be prevented from early seizure due to poor lubrication or contamination, and the life of the bearing can be improved.
Moreover, this uneven | corrugated structure may be the form which each concave part and convex part are not comprised circularly but meandered. Further, the concave portion and the convex portion may have different sizes (depth, height, width, etc.). Furthermore, the concave portion and the convex portion may be provided intermittently.

Example 1 which is one embodiment of the rolling bearing of the present invention is shown, (a) is a sectional view showing a part of the rolling bearing omitted and enlarged, and (b) is a sealing mechanism of (a). It is sectional drawing which expands and shows the component part of. Example 2 is shown, (a) is a cross-sectional view showing, in an enlarged manner, a component part of a sealing mechanism provided with a tapered inclined surface in the bearing inner direction on the outer diameter side of the retaining ring, (b), It is sectional drawing which expands and shows the component part of the sealing mechanism which provided the inclined surface on a taper over the whole surface of the bearing inner direction of a retaining ring. FIG. 10 is a cross-sectional view showing Example 3 and showing an enlarged configuration of another example of the sealing mechanism. The modification of Example 1 is shown, (a) shows the case where the inner wall surface of the retaining ring groove is in contact with a part of the retaining ring, and (b) shows the inner wall surface of the retaining ring groove as the retaining ring. It is a principal part enlarged view which shows the case where it is not contacting. The modification of Example 2 is shown, (a) shows the case where the inner wall surface of the retaining ring groove is in contact with a part of the retaining ring, and (b) shows the inner wall surface of the retaining ring groove as the retaining ring. It is a principal part enlarged view which shows the case where it is not contacting. The modification of Example 3 is shown, (a) shows the case where the inner wall surface of a retaining ring groove is contacting a part of retaining ring, (b) shows the inner wall surface of a retaining ring groove as a retaining ring. It is a principal part enlarged view which shows the case where it is not contacting. It is sectional drawing which abbreviate | omits and shows an enlarged view of Example 4, and is one form which installed the floating ring between rollers. FIG. 10 is a cross-sectional view showing a part of the fifth embodiment with a part omitted, and (a) is an embodiment in which the outer collar of the inner ring is a separate collar and the sealing mechanism constituting the present invention is incorporated in the collar. , (B) is an embodiment in which the inner collar of the outer ring is eliminated, a floating ring is installed between the rollers, the outer collar of the inner ring is a separate collar, and the sealing mechanism constituting the present invention is incorporated in the collar ring. It is. It is sectional drawing which abbreviate | omits and shows a part expanded Example 6, and is one Embodiment which applied this invention to the double row tapered roller bearing. In one application example of the rolling bearing of the present invention, (a) is a schematic side view showing a configuration example of a rolling roll group of a multi-stage rolling mill, and (b) is a schematic front view showing a configuration example around a backing roll axis. is there. It is sectional drawing of the rolling bearing which concerns on the prior art 1, (a) is sectional drawing which abbreviate | omits and shows the structure of the conventional rolling bearing incorporated in the backing roll axis | shaft partially, (b) is ( It is sectional drawing which expands and shows the structural part of the sealing mechanism of a).

Explanation of symbols

14 Inner ring (stationary wheel)
16 Outer ring (rotating wheel)
16b Retaining ring groove 18 Rolling element 22 First seal member 23b Annular portion 24 of the first seal member Second seal member 24a Core metal 24b of the second seal member Elastic member 24c of the second seal member Second An annular portion 24g of the sealing member of the first protrusion 26 A retaining ring 26a A tapered inclined surface Lp A sealing lip of the second sealing member

Claims (4)

A stationary wheel maintained in a non-rotating state, a rotating wheel that rotates opposite to the stationary wheel, a plurality of rolling elements that are rotatably incorporated between the stationary wheel and the rotating wheel, and a stationary wheel and a rotating wheel A sealing mechanism for sealing the inside of the bearing partitioned between and from the outside of the bearing,
The sealing mechanism is
A first seal member that includes a ring portion that is fixed to one of the rotating wheel and the stationary wheel and includes an annular core;
A ring member is provided that is fixed to the other of the rotating wheel and the stationary wheel and includes an annular cored bar and an elastic member that covers the cored bar, and the annular part is a first seal member. And a second seal member disposed so as to be opposed in the axial direction.
The second seal member extends integrally from the predetermined region of the elastic member constituting the annular portion in an inclined manner toward the annular portion of the first seal member, and the annular portion of the first seal member An annular seal lip that slides into contact to form a contact seal area,
One of the first seal member and the second seal member is fixed by an annular retaining ring fitted in a circumferential groove formed in a rotating wheel or a stationary wheel provided with the seal member. A rolling bearing having a structure to be
One or both surfaces on the bearing inner side or bearing outer side of the retaining ring are tapered toward the outer periphery of the retaining ring, or the groove portion of the outer ring on which the retaining shaft is installed tapers toward the inner periphery. A rolling bearing characterized by being formed into a shape.   The rolling ring according to claim 1, wherein the stationary wheel is configured as an inner ring disposed opposite to the inner side of the rotating ring, and the rotating wheel is configured as an outer ring disposed opposite to the outer side of the inner ring. bearing.   The rolling bearing according to claim 1, wherein lubrication is performed inside the bearing using oil or oil and compressed air. A rolling bearing used in a multi-stage rolling mill for rolling steel materials,
The rolling bearing according to claim 1, wherein the multi-stage rolling mill includes a rolling roller group for rolling the steel material, and the rolling bearing is assembled to a backing roll shaft of the rolling roller group. .

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