Rolling bearings
The rolling bearing design with a flange and projection on the inner ring effectively manages lubricant flow and simplifies manufacturing by preventing axial displacement and lubricant leakage, ensuring consistent lubrication in steel rolling mills.
Patent Information
- Authority / Receiving Office
- JP · JP
- Patent Type
- Applications
- Current Assignee / Owner
- NSK LTD
- Filing Date
- 2024-10-23
- Publication Date
- 2026-05-11
AI Technical Summary
Existing rolling bearings for steel rolling mills face issues with lubricant flow-out due to axial displacement of the rolling element cage, leading to insufficient lubrication and increased manufacturing complexity.
A rolling bearing design with an outer ring member having double rows of raceway surfaces, an inner ring member with double rows of raceway surfaces, and an integrally formed annular projection on the inner ring to prevent lubricant flow between opposing raceway surfaces, using a mechanism that includes a flange and projection to manage lubricant distribution.
Prevents lubricant flow-out while ensuring easy manufacturing by reducing the number of parts and simplifying assembly, maintaining effective lubrication across the bearing's axial direction.
Smart Images
Figure 2026076007000001_ABST
Abstract
Description
Technical Field
[0001] The present invention relates to a rolling bearing.
Background Art
[0002] Generally, a steel rolling mill includes a plurality of rolling rolls for performing rolling processing in the thickness direction of a workpiece to be rolled, and a plurality of edger rolls for performing rolling processing in the width direction of the workpiece to be rolled.
[0003] FIG. 5 is a cross-sectional view schematically showing an edger roll for a steel rolling mill. As shown in FIG. 5, the edger roll 250 is composed of a pair of vertical rolls 200 installed such that the rotation axis faces the vertical direction. The pair of vertical rolls 200 are arranged such that the outer peripheral surface of the roll portion 201 contacts the side surface of the workpiece to be rolled 500 extending in the thickness direction. Further, a shaft portion 202 connected to the roll portion 201 in the axial direction is rotatably supported by a chuck 203 and a bearing 230.
[0004] As in the bearing 230 shown in FIG. 5, a vertical multi-row rolling bearing applied to a vertical roll for a steel rolling mill is installed such that the rotation axis faces the vertical direction, and a lubricant (grease) for lubricating the upper rolling element row of the rolling element rows arranged in two upper and lower rows in the vertical direction may flow down to the lower rolling element row by its own weight when the bearing stops or when the bearing rotates, resulting in insufficient lubrication of the upper rolling element row.
[0005] As a rolling bearing for solving such a lubricant flow problem, for example, as described in Patent Document 1, there is a rolling bearing in which a flange portion is integrally formed on the outer diameter surface of the annular portion of the rolling element cage, and the lubricant holding spaces of the upper rolling element row and the lower rolling element row are partitioned by this flange portion.
[0006] Further, in the rolling bearing described in Patent Document 2, a structure is adopted in which an annular flange member is engaged with the inner ring to partition the lubricant holding spaces of the upper rolling element row and the lower rolling element row.
Prior Art Documents
Patent Documents
[0007] [Patent Document 1] Japanese Patent Publication No. 2005-76724 [Patent Document 2] Japanese Patent Publication No. 2013-032837 [Overview of the project] [Problems that the invention aims to solve]
[0008] However, in a structure like the rolling bearing described in Patent Document 1, where a flange portion is formed on the annular part of the rolling element cage to separate the lubricant-holding space between the upper and lower rolling element rows, the rolling element cage may be displaced axially and radially as the rolling bearing rotates, causing the gap between the flange portion and the outer ring to increase. As a result, the lubricant from the upper rolling element row, which is ejected radially outward by centrifugal force, may flow down through the gap between the flange portion and the outer ring.
[0009] Furthermore, in structures such as the rolling bearing described in Patent Document 2, in which an annular flange member is engaged with the inner ring, there was room for improvement, as the number of parts increased and manufacturing man-hours were required.
[0010] The present invention has been made in view of the above problems, and its purpose is to provide a rolling bearing that can prevent lubricant from flowing out from the space between the opposing inner ring raceway surfaces and the outer ring raceway surfaces into other spaces adjacent in the axial direction, and that is easy to manufacture. [Means for solving the problem]
[0011] The above objective of the present invention is achieved by the following configuration. (1) An outer ring member having double rows of outer ring raceway surfaces on its inner circumferential surface, An inner ring member having double rows of inner ring raceway surfaces on its outer circumferential surface, A plurality of rolling elements are arranged between the outer ring raceway surface and the inner ring raceway surface, which are opposite to each other, A retainer that holds the plurality of rolling elements so that they can roll, A rolling bearing equipped with, The inner ring member is A flange formed between the two rows of inner ring raceway surfaces adjacent in the axial direction, An annular projection extends radially outward from the outer circumferential surface of the flange and is integrally formed with the inner ring member, It has, When the axial width of the radially inner end of the projection connected to the outer circumferential surface of the flange is A, and the axial width of the radially outer end of the projection is B, then A <Bである A rolling bearing characterized by the following. [Effects of the Invention]
[0012] According to the present invention, it is possible to prevent lubricant from flowing out from the space between the opposing inner ring raceway surfaces and the outer ring raceway surfaces into other spaces adjacent in the axial direction, thereby providing an easy-to-manufacture rolling bearing. [Brief explanation of the drawing]
[0013] [Figure 1] Figure 1 is a cross-sectional view of a part of the vertical roll of the rolling mill according to this embodiment. [Figure 2] Figure 2 shows a cross-section of the tapered roller bearing according to this embodiment, perpendicular to the circumferential direction. [Figure 3] Figure 3 shows a cross-section perpendicular to the circumferential direction of a tapered roller bearing according to a modified example of this embodiment. [Figure 4] Figure 4 shows a cross-section perpendicular to the circumferential direction of a tapered roller bearing according to a comparative example of this embodiment. [Figure 5] Figure 5 is a schematic cross-sectional view of an edger roll for a steel rolling mill. [Modes for carrying out the invention]
[0014] FIG. 1 is a cross-sectional view showing a part of a vertical roll of a rolling mill according to the present embodiment. As shown in FIG. 1, the vertical roll 100 of the present embodiment includes a roll portion 1, a shaft portion 2 connected to the roll portion 1, a chuck 3 which is a housing, and a double-row tapered roller bearing 30 which is a rolling bearing disposed between the shaft portion 2 and the chuck 3.
[0015] Here, the tapered roller bearing 30 according to the present embodiment is for a vertical roll in a rolling mill of steel facilities. In the vertical roll 100, a side surface extending in the thickness direction of a plate-shaped steel member (not shown), which is a material to be rolled, that is, a surface extending in the vertical direction is rolled to have a predetermined width dimension. Therefore, the rotation axes of the vertical roll 100 and the rolling bearing 30 are arranged to face the vertical direction. Hereinafter, with respect to the axial direction, the lower side in the vertical direction, that is, the direction in which gravity acts (the lower side in FIG. 1) is referred to as the lower side in the axial direction. Also, the side opposite to the lower side in the axial direction (the upper side in FIG. 1) is referred to as the upper side in the axial direction.
[0016] The tapered roller bearing 30 includes an outer ring member 36 composed of a pair of outer rings 31a and 31b fitted to the inner peripheral surface of the chuck 3 and an outer ring spacer 35, an inner ring member composed of a single inner ring 32 fitted to the outer peripheral surface of the shaft portion 2, tapered rollers 33, 33 which are rolling elements arranged in a double row between the inner peripheral surfaces of the pair of outer rings 31a and 31b and the outer peripheral surface of the single inner ring 32, and a pair of cages 34, 34 which hold the double row of tapered rollers 33, 33 so as to be rollable at equal intervals in the circumferential direction.
[0017] The outer ring member 36 is arranged such that the outer ring 31a, the spacer 35 between the outer rings, and the outer ring 31b are coaxially aligned from the upper side in the axial direction. The spacer 35 between the outer rings is sandwiched between the pair of outer rings 31a and 31b. Here, the pair of outer rings 31a and 31b each have outer ring raceway surfaces 41a and 41b on their inner peripheral surfaces, which constitute the double-row outer ring raceway surfaces of the outer ring member 36. Also, the single inner ring 32 has double-row inner ring raceway surfaces 51a and 51b on its outer peripheral surface. Therefore, the tapered roller bearing 30 is a double-row tapered roller bearing, and a plurality of tapered rollers 33 and 33 are respectively arranged between the outer ring raceway surface 41a and the inner ring raceway surface 51a facing each other in the radial direction, and between the outer ring raceway surface 41b and the inner ring raceway surface 51b facing each other in the radial direction. Hereinafter, the space between the outer ring raceway surface 41a and the inner ring raceway surface 51a is referred to as the upper axial row, and the space between the outer ring raceway surface 41b and the inner ring raceway surface 51b is referred to as the lower axial row. Note that the configuration of the outer ring member 36 and the inner ring member may be changed depending on the type of rolling bearing, for example, instead of an inner ring member consisting of a single inner ring 32, an inner ring member consisting of a pair of inner rings may be used, etc.
[0018] The double-row tapered rollers 33 and 33 have a taper. The tapered rollers 33 in the upper axial row are arranged in a direction where the diameter increases as they go toward the lower side in the axial direction. Also, the tapered rollers 33 in the lower axial row are arranged in a direction where the diameter increases as they go toward the upper side in the axial direction. That is, the tapered rollers 33 and 33 are arranged such that the heads of the tapered rollers 33 in the upper axial row and the lower axial row face each other.
[0019] The pair of cages 34 and 34 are respectively arranged in the upper axial row and the lower axial row. Also, the pair of cages 34 and 34 each have two annular members and a plurality of column portions arranged at equal intervals in the circumferential direction so as to connect the two annular members, and hold the plurality of tapered rollers 33 and 33 arranged in double rows in a freely rotatable manner.
[0020] The pair of outer rings 31a and 31b are positioned axially by a pair of outer ring retaining members 6 and 9 and an outer ring spacer 35 fixed to both axial ends of the chock 3. In addition, a cover member 5 is provided fixed to the chock 3 on the axial lower side of the chock 3 so as to cover the outer circumferential surface and a portion of the axial lower end surface of the outer ring retaining member 9.
[0021] The inner ring 32 is positioned axially by a pair of inner ring retaining members 7 and 10. The inner ring retaining member 7 abuts against a locking member 13 fastened to the shaft portion 2, and the inner ring retaining member 10 abuts against a shoulder portion 12 formed between the shaft portion 2 and the roll portion 1, thereby restricting their axial movement. The inner ring retaining member 7 is also called a thrust collar, and the inner ring retaining member 10 is also called a fret ring.
[0022] Furthermore, the chock 3 has a lubrication passage 4 for supplying lubricant to the tapered roller bearing 30 from the outside. The lubrication passage 4 extends from the axial upper end of the chock 3 to the inner circumferential surface of the chock 3 and communicates with a lubrication hole 37 provided in the outer ring spacer 35 and a lubrication groove 8 provided on the axial lower end face of the outer ring retaining member 6. The lubrication hole 37 provided in the outer ring spacer 35 penetrates radially through the axial center of the outer ring spacer 35 and communicates with the internal space S1 of the tapered roller bearing 30. Here, the internal space S1 is the space enclosed by the inner circumferential surface of the outer ring member 36 (outer rings 31a, 31b and outer ring spacer 35) and the outer circumferential surface of the inner ring member (inner ring 32). In other words, the internal space S1 is the space from the axial upper opening between the outer ring 31a and the inner ring 32 to the axial lower opening between the outer ring 31b and the inner ring 32. Furthermore, the lubrication groove 8 provided in the outer ring retaining member 6 penetrates radially through the axial lower end of the outer ring retaining member 6 and communicates with the axial upper end of the tapered roller bearing 30 and the internal space S2 enclosed by the outer ring retaining member 6 and the inner ring retaining member 7. Moreover, the internal space S2 is in contact with the axial upper opening of the tapered roller bearing 30, and the internal space S1 and the internal space S2 are in communication.
[0023] As described above, the lubricant supplied from outside the chock 3 passes through the lubrication passage 4 and then through the lubrication groove 8 of the outer ring retaining member 6 or the lubrication hole 37 of the outer ring spacer 35. The lubricant that reaches the internal space S2 through the lubrication groove 8 of the outer ring retaining member 6 flows down into the internal space S1 by its own weight and is supplied to the upper axial row. The lubricant supplied from the lubrication hole 37 of the outer ring spacer 35 is supplied to the lower axial row of the internal space S1.
[0024] Furthermore, the outer ring retaining member 9 and the inner ring retaining member 10, and the outer ring retaining member 6 and the inner ring retaining member 7, are radially opposite each other with a small gap between them, forming labyrinth seals 14 and 15. This prevents foreign matter from entering the chock 3 and tapered roller bearing 30 from the outside, and prevents lubricant from leaking out from the inside.
[0025] Here, since the tapered roller bearing 30 is installed with its axial direction oriented vertically, there is a concern that the lubricant supplied to the upper axial row in the internal space S1 may flow down to the lower axial row. In response to this, the present invention provides a mechanism on the inner ring 32 of the tapered roller bearing 30 to prevent the lubricant from flowing down. This will be explained in detail below.
[0026] Figure 2 shows a cross-section of the tapered roller bearing according to this embodiment, perpendicular to the circumferential direction. In Figure 2, the right side is considered the upper axial side, and the left side is considered the lower axial side.
[0027] As shown in Figures 1 and 2, the inner ring 32 has a large flange portion 52 formed between two adjacent inner ring raceway surfaces 51a and 51b in the axial direction, which slides against the heads of the two rows of tapered rollers 33, 33. Furthermore, the inner ring 32 has an annular projection portion 53 formed to project radially outward from the outer circumferential surface of the large flange portion 52. The large flange portion 52 and the projection portion 53 are integrally formed with the inner ring 32. The projection portion 53 is formed over the entire circumference of the outer circumferential surface of the large flange portion 52 and has a smaller axial width than the large flange portion 52. Also, the projection portion 53 does not contact the heads of the two rows of tapered rollers 33, 33 or the pair of retainers 34, 34. Furthermore, the radially outer end of the projection portion 53 faces the inner circumferential surface of the outer ring spacer 35 radially with a small gap between them.
[0028] The internal space S1 formed between the outer ring member 36 and the inner ring 32 of the tapered roller bearing 30 is divided by a projection 53 into an internal space S1a axially above the projection 53, an internal space S1b axially below the projection 53, and a gap S1c between the radially outer end of the projection 53 and the inner circumferential surface of the outer ring spacer 35. The radial width of the gap S1c is set to a size that suppresses the flow of lubricant from the internal space S1a to the internal space S1b, and prevents the projection 53 from coming into contact with the outer ring spacer 35 when the tapered roller bearing 30 rotates.
[0029] As described above, the intermediate outer ring seat 35 has a grease supply hole 37 for supplying lubricant. At least one grease supply hole 37 is formed in the intermediate outer ring seat 35, and a plurality of grease supply holes 37 may be formed side by side in the circumferential direction. In this example, the axial positions of the grease supply hole 37 of the intermediate outer ring seat 35 and the radially outer end of the protruding portion 53 overlap when viewed in the radial direction. That is, the lubricant supplied from the grease supply hole 37 slowly passes through a part of the clearance S1c between the radially outer end of the protruding portion 53 and the inner peripheral surface of the intermediate outer ring seat 35, and is supplied to the internal space S1b on the lower side in the axial direction. Note that the axial width of the protruding portion 53 may be formed smaller than that in the example of FIG. 2, and further, the grease supply hole 37 of the intermediate outer ring seat 35 may be provided closer to the lower side in the axial direction so that the axial positions of the protruding portion 53 and the grease supply hole 37 do not overlap. In this case, the lubricant is directly supplied from the grease supply hole 37 of the intermediate outer ring seat 35 to the internal space S1b without passing through the clearance S1c.
[0030] When the axial width of the radially inner end of the protruding portion 53 connected to the outer peripheral surface of the large flange portion 52 is A, and the axial width of the radially outer end of the protruding portion 53 is B, A < B. In the present embodiment, the protruding portion 53 has an axially symmetric shape with respect to the axial center P, and the axial width of the protruding portion 53 gradually increases from the radially inner end toward the radially outer end. That is, when the surface of the protruding portion 53 in contact with the internal space S1a is the axially upper surface 53a, the axially upper surface 53a is inclined so as to face upward in the axial direction toward the radially outer side. Thereby, it is possible to prevent the lubricant from flowing radially outward along the axially upper surface 53a due to centrifugal force, and it is possible to prevent the lubricant from flowing down from the internal space S1a toward the internal space S1b. Further, when the surface of the protruding portion 53 in contact with the internal space S1b is the axially lower surface 53b, the axially lower surface 53b is inclined in a direction toward the lower side in the axial direction toward the radially outer side. By making the protruding portion 53 have an axially symmetric shape with respect to the axial center P, when the tapered roller bearing 30 is incorporated into the vertical roller 100, the orientation of the tapered roller bearing 30 is not restricted, and handling becomes easy.
[0031] The shape of the protrusion 53 is not limited to the shape described above; the axial upper surface 53a and the axial lower surface 53b may be curved surfaces with a circular arc cross-section, etc. Also, the protrusion 53 does not necessarily have to be symmetrical with respect to the axial center P.
[0032] As a method for forming the large flange portion 52 and the protruding portion 53 which are integrally formed with the inner ring 32, for example, one method is to perform turning on a forged metal material using a lathe or the like to cut out the large flange portion 52 and the protruding portion 53.
[0033] Next, the assembly method of the tapered roller bearing 30 according to this embodiment will be described. First, the tapered rollers 33 and the cage 34 are combined to form a single unit. Then, the two sets of tapered rollers 33 and cage 34 are assembled onto a single inner ring 32 from the axial upper side and the axial lower side. After that, the outer ring 31a and outer ring 31b are assembled onto the inner ring 32, tapered rollers 33,33 and cages 34,34 from the axial upper side and the axial lower side, respectively. At this point, the outer ring spacer 35 is not assembled. This state is left to stand for a certain period of time to stabilize the contact between the outer rings 31a,31b and inner ring 32 and the tapered rollers 33,33. Then, the dimensions of the outer ring spacer 35 before assembly are adjusted to match the axial gap between the outer ring 31a and outer ring 31b. After that, either the outer ring 31a or outer ring 31b is removed once, and the outer ring spacer 35 is assembled from the axial side. Finally, reassemble the outer ring 31a or outer ring 31b that was removed.
[0034] The following describes modifications of this embodiment. Figure 3 is a diagram showing a cross-section perpendicular to the circumferential direction of a tapered roller bearing according to a modification of this embodiment. As shown in Figure 3, the projection 53 may have a shape that extends radially outward from a radially inner end connected to the outer circumferential surface of the large flange 52, and has a base 54 whose axial width is equal to the axial width A of the radially inner end, and a widening portion 55 provided radially outward of the base 54 and having a larger axial width than the base 54. The projection 53 in this example is symmetrical with respect to the axial center P and has a T-shaped cross-section. The base 54 has an axial upper surface 54a that is in contact with the axially upper internal space S1a, and an axial lower surface 54b that is in contact with the axially lower internal space S1b, and the axial upper surface 54a and the axial lower surface 54b are parallel to each other. The widened portion 55 is shaped to protrude axially upward and axially downward from the radially outer ends of the axially upper surface 54a and axially lower surface 54b of the base portion 54, respectively. Furthermore, the axial width of the widened portion 55 is equal to the axial width B of the radially outer end of the protruding portion 53 and is constant regardless of the radial position.
[0035] In this example as well, the shape of the protruding portion 53 does not have to be symmetrical with respect to the axial center P, and the widened portion 55 may have a shape that protrudes only upward in the axial direction. Furthermore, the axial tip of the widened portion 55 may have a rounded shape.
[0036] The effects of this embodiment will be described below with reference to comparative examples. Figure 4 is a cross-sectional view perpendicular to the circumferential direction of a tapered roller bearing according to a comparative example of this embodiment, which is provided with a structure to prevent lubricant from flowing down the outer ring. In the comparative example shown in Figure 4, an annular member 153 is provided on the inner circumferential surface of the outer ring spacer 35 of the tapered roller bearing 130. The radially inner end of the annular member 153 is close to the outer circumferential surface of the large flange portion 52 of the inner ring 32, and a small radial gap is formed between the outer circumferential surface of the large flange portion 52 and the radially inner end of the annular member 153. The outer ring spacer 35 has a female screw hole that penetrates radially, and the annular member 153 has a female screw hole at its radially outer end. The annular member 153 is screwed to the outer ring spacer 35 using a screw 154.
[0037] The specific method for fixing the annular member 153 is as follows: First, the annular member 153 is assembled coaxially to a single inner ring 32. Next, the two sets of tapered rollers 33 and cages 34, now in a single unit state, are assembled to the single inner ring 32 from the axial upper and axial lower sides. After that, the outer rings 31a and 31b are assembled to the inner ring 32, tapered rollers 33, 33, and cages 34, 34 from the axial upper and axial lower sides. This state is left to stand for a certain period of time to stabilize the contact between the outer rings 31a, 31b and inner ring 32 and the tapered rollers 33. Then, the dimensions of the outer ring spacer 35 are adjusted to match the axial gap between the outer rings 31a and 31b before assembly. After that, either the outer ring 31a or the outer ring 31b is removed, and the outer ring spacer 35 is assembled from the axial side. Next, the outer ring spacer 35 and the pre-assembled annular member 153 are screwed together, and the screw 154 is crimped to prevent it from coming loose. Finally, the outer ring 31a or outer ring 31b that was removed is reassembled.
[0038] In the example above, the screw 154 is typically a set screw with a hexagonal socket and no head (a so-called grub screw). This is to ensure that the screw 154 does not protrude radially outward from the outer surface of the outer ring spacer 35. However, if the crimping process for the screw 154 is insufficient or omitted, the screw 154 may come loose from the outer ring spacer 35 and protrude radially outward. This may prevent the tapered roller bearing 130 from being assembled into the chock 3, or it may damage the inner surface of the chock 3.
[0039] As a variation of the comparative example, if the annular member 153 and the outer ring spacer 35 are integrated, handling may be impaired when adjusting the axial dimensions of the outer ring spacer 35. Also, when assembling the outer ring spacer 35 from the axial direction, it may interfere with the tapered roller 33, making assembly difficult.
[0040] On the other hand, the tapered roller bearing 30 according to this embodiment has a projection 53 that protrudes radially outward from the outer circumferential surface of the large flange portion 52 of the inner ring 32 and is integrally formed. This eliminates the need for set screws and reduces the number of parts compared to the tapered roller bearing 130 shown in the comparative example and the rolling bearing in which the flange portion is engaged with the inner ring described in Patent Document 2. Furthermore, the tapered roller bearing 30 is easy to manufacture because it is easy to handle when assembling the outer ring spacer 35.
[0041] In the tapered roller bearing 30 according to this embodiment, a projection 53 is integrally formed on the inner ring 32, and the axial width of the radially outer end of the projection 53 is made larger than that of the radially inner end. This prevents the lubricant from reaching the radially outer side due to centrifugal force and flowing down from the internal space S1a including the axially upper row towards the internal space S1b including the axially lower row, and also provides a rolling bearing that is easy to manufacture.
[0042] It should be noted that the present invention is not limited to the embodiments illustrated above, and can be modified as appropriate without departing from the spirit of the invention. For example, the shape of the protrusion 53 is symmetrical with respect to the axial center P in this embodiment, but it does not have to be symmetrical. That is, the structure should be such that the radial outer end of the protrusion 53 protrudes axially upward more than the radial inner end, thereby preventing the lubricant in the axially upward internal space S1a from reaching the radial outer end of the protrusion 53 by centrifugal force. Also, the axial width of the protrusion 53 may be formed to be smaller than in the illustrated example. Furthermore, although a tapered roller bearing 30 is used in this embodiment, the protrusion 53 may also be provided on a double-row cylindrical roller bearing or a double-row ball bearing, etc. Therefore, the shape of the protrusion 53 and the large flange 52 can be appropriately modified depending on the type of rolling bearing to which it is applied. Moreover, the present invention can also be applied when the rotation axis of these rolling bearings is oriented horizontally. In this case, the protrusion 53 should have a shape in which the radial outer end widens in any axial direction.
[0043] As described above, the following matters are disclosed in this specification: (1) An outer ring member having double rows of outer ring raceway surfaces on its inner circumferential surface, An inner ring member having double rows of inner ring raceway surfaces on its outer circumferential surface, A plurality of rolling elements are arranged between the outer ring raceway surface and the inner ring raceway surface, which are opposite to each other, A retainer that holds the plurality of rolling elements so that they can roll, A rolling bearing equipped with, The inner ring member is A flange formed between the two rows of inner ring raceway surfaces adjacent in the axial direction, An annular projection extends radially outward from the outer circumferential surface of the flange and is integrally formed with the inner ring member, It has, When the axial width of the radially inner end of the projection connected to the outer circumferential surface of the flange is A, and the axial width of the radially outer end of the projection is B, then A <Bである A rolling bearing characterized by the following. This configuration prevents lubricant from flowing out of the space between the opposing inner and outer ring raceway surfaces into other spaces adjacent in the axial direction, thus providing an easy-to-manufacture rolling bearing.
[0044] (2) The rolling bearing according to (1), characterized in that the axial width of the protrusion increases as it extends radially outward. This configuration makes it less likely for lubricant adhering to the protrusion to flow radially outward from the protrusion, and makes it easier to prevent lubricant from flowing out from the space between the opposing inner and outer ring raceway surfaces into other spaces adjacent in the axial direction.
[0045] (3) The protruding portion is A base portion is formed to extend radially outward from the radially inner end, and has an axial width equal to that of the radially inner end, A widened portion is provided radially outward from the base, and has a larger axial width than the base, has The rolling bearing according to (1), characterized in that... This configuration makes it less likely for lubricant adhering to the protrusion to flow radially outward from the protrusion, and makes it easier to prevent lubricant from flowing out from the space between the opposing inner and outer ring raceway surfaces into other spaces adjacent in the axial direction.
[0046] (4) The rolling bearing is for a rolling mill in a steelworks, The rotation axis of the rolling bearing is positioned to face vertically. A rolling bearing according to any one of (1) to (3), characterized by the above. This configuration prevents lubricant from flowing vertically downward through the space between the opposing inner and outer ring raceway surfaces. [Explanation of Symbols]
[0047] 1 Roll section 2. Shaft section 3 Chock 4 Greasing path 5. Lid member 6,9 Outer ring retaining member 8 Greasing groove 7,10 Inner ring retaining member 13 Locking member 14,15 Labyrinth Seal 30 bearings 31a, 31b outer ring 32 Inner ring (inner ring component) 34 Cage 35 Outer wheel spacer 36 Outer ring member 37 Greasing hole 41a, 41b Outer ring raceway surface 51a, 51b Inner ring track surface 52 Large Tsuba (Tsuba) 53 Protrusion 54 Base 55 Widening section 100 vertical rolls 153 Annular member S1,S2 internal space
Claims
1. An outer ring member having double rows of outer ring raceway surfaces on its inner circumferential surface, An inner ring member having double rows of inner ring raceway surfaces on its outer circumferential surface, A plurality of rolling elements are arranged between the outer ring raceway surface and the inner ring raceway surface, which are opposite to each other, A retainer that holds the plurality of rolling elements so that they can roll, A rolling bearing equipped with, The inner ring member is A flange formed between the two rows of inner ring raceway surfaces adjacent in the axial direction, An annular projection extends radially outward from the outer circumferential surface of the flange and is integrally formed with the inner ring member, It has, When A is the axial width of the radially inner end of the projection connected to the outer circumferential surface of the flange, and B is the axial width of the radially outer end of the projection, then A < B. A rolling bearing characterized by the following.
2. The rolling bearing according to claim 1, characterized in that the axial width of the protrusion increases as it extends radially outward.
3. The aforementioned protrusion is A base portion is formed to extend radially outward from the radially inner end, and has an axial width equal to that of the radially inner end, A widened portion is provided radially outward from the base, and has a larger axial width than the base, has The rolling bearing according to claim 1, characterized in that...
4. The aforementioned rolling bearing is for a rolling mill in a steelmaking facility, The rotation axis of the rolling bearing is positioned to face vertically. A rolling bearing according to any one of claims 1 to 3, characterized in that