JP2014009707A - Solid lubrication rolling bearing - Google Patents

Abstract

PROBLEM TO BE SOLVED: To prevent or suppress the scattering of abrasion powder of a solid lubricant to the outside by closing the abrasion power inside a bearing, in a solid lubrication rolling bearing.SOLUTION: In order to prevent or suppress the scattering of abrasion powder of a solid lubricant generated inside a solid lubrication rolling bearing 10 to the outside of the bearing, an outer peripheral edge part 24 of a shield plate 23 is attached to an outer ring 11 of the rolling bearing 10. In the solid lubrication rolling bearing 10 approaching or contacting an inner peripheral edge part 27 of the shield plate 23 to or with an inner ring 12 side, a portion between the outer peripheral edge part 24 and inner peripheral edge part 27 of the shield plate 23 is bent to be opened inward the bearing, a peripheral groove 28 whose bottom surface projects to a bearing width outside is formed, and a retention part 29 for the abrasion powder is formed by the peripheral groove 28.

Description

  The present invention relates to a rolling bearing in which the inside of the bearing is lubricated by a solid lubricant, that is, a solid lubricated rolling bearing, and is used, for example, as a bearing for supporting a tenter clip of a film stretching machine.

  A film stretching machine is a machine that heats and melts a stretched material such as vinyl and stretches it thinly, and a clip that sandwiches the stretched material is a tenter clip (Patent Document 1). Guide rails are installed on both sides of the drawing line so that the distance gradually increases in the traveling direction, and tenter clips are mounted on the guide rails via guide rollers so as to be able to run. When running with the tenter clips on both sides sandwiching both side edges of the stretched material, the stretched material is stretched thinly in the width direction. The guide roller is a rolling bearing that uses an outer ring as a roller.

  When the atmospheric temperature in which the tenter clip is used is 150 to 250 ° C., heat-resistant grease, for example, fluorine grease is used for lubrication of the rolling bearing, and a steel plate shield plate or fluorine rubber is used as a sealing material. Is used.

  When the stretched material is PEEK (polyether, ether, ketone) resin, PI (polyimide) resin, etc., the ambient temperature becomes extremely high (up to 400 ° C), so a solid lubrication system is used for lubrication of rolling bearings. (Patent Document 2).

  Solid lubrication type rolling bearings, that is, solid lubrication rolling bearings, for example, have a cage surface formed by a solid lubricant or a composite material containing the same, and a separator formed by a solid lubricant between rolling elements. There is what I did. Examples of the solid lubricant in this case include graphite, tungsten disulfide, and molybdenum disulfide.

  The rolling bearing is provided with a shield plate between the inner and outer rings in order to prevent dust and foreign matter from entering from the outside. The structure is as shown in FIG. 19 attached, and the shield plate 1 is fitted and fixed to the mounting groove 4 provided on the inner diameter surface of the outer ring 3 at the outer peripheral edge 2 thereof.

  The inner peripheral edge 5 of the shield plate 1 is bent inward, and the inner peripheral edge 5 faces the seal groove 7 provided on the outer diameter surface of the inner ring 6 with a predetermined gap. A large number of rolling elements 8 are interposed between the raceway grooves of the inner ring 6 and the outer ring 3 and are held at predetermined intervals by a cage 9. A labyrinth seal is formed by a gap between the inner peripheral edge portion 5 and the seal groove 7, a gap δ between the inner peripheral edge portion 5 and the shoulder outer peripheral portion 6a, and the like.

JP 2007-232089 A JP 2009-281532 A

  However, since the solid lubricant rolling bearing generates wear powder of the solid lubricant with the operation of the bearing, it is inevitable that the wear powder is scattered outside the bearing through the gap δ of the shield plate 1.

  In the film stretching machine, it is strictly forbidden for foreign matter to adhere to the film as the stretching material, but the conventional shield plate 1 is a non-contact type and has a gap δ, so that the scattering of wear powder is prevented or suppressed. There was a problem that the effect to do was insufficient.

  In view of this, an object of the present invention is to prevent or suppress scattering to the outside in a solid lubricated rolling bearing by confining the wear powder of the solid lubricant inside the bearing.

  In order to solve the above-described problems, a solid lubricated rolling bearing according to the present invention is provided with the above-described rolling in order to prevent or suppress the scattering of solid lubricant wear powder generated inside the solid lubricated rolling bearing to the outside of the bearing. A solid lubricated rolling bearing in which the fixed peripheral edge of the annular shield plate is attached to the shoulder of one of the bearing rings, and the free peripheral edge of the shield plate is brought close to or in contact with the shoulder of the other bearing ring In this case, a portion between the fixed peripheral edge portion and the free peripheral edge portion of the shield plate is bent and opened toward the inside of the bearing, and a circumferential groove with a bottom surface protruding outside the bearing width is formed. This is the one where a staying part of the wear powder is formed.

  By forming a deep circumferential groove in the shield plate, a large volume retention portion is formed, so that abrasion powder generated inside the bearing can be sufficiently retained, and scattering to the outside is prevented or suppressed.

  Further, in order to solve the above-mentioned problems, the solid lubricated rolling bearing according to the present invention is configured to prevent or suppress scattering of wear powder of solid lubricant generated outside the solid lubricated rolling bearing to the outside of the bearing. Solid lubrication in which a fixed peripheral edge of an annular shield plate is attached to the shoulder of one of the rolling bearings, and the free peripheral edge of the shield plate is brought close to or in contact with the shoulder of the other bearing ring In a rolling bearing, a free side peripheral portion forming the peripheral groove by bending a portion between the fixed side peripheral portion and the free side peripheral portion of the shield plate to form a peripheral groove opened toward the bearing internal direction. A shallow bent portion is provided at the front end of each of the two, and a stay portion for wear powder is formed by the circumferential groove including the bent portion.

  In this case, the depth of the circumferential groove does not matter, but a shallow folded bent portion is provided at the distal end of the peripheral edge of the free side of the circumferential groove, and a stay portion for wear powder is formed by the circumferential groove including the bent portion. . The volume of the circumferential groove is increased by the folded portion, and at the same time, the wear powder staying in the staying portion is prevented from escaping.

  By adopting a configuration in which a folded portion that is folded deeper at the tip of the folded portion is provided, or a configuration in which the bottom surface of the circumferential groove protrudes outside the bearing width, the volume of the circumferential groove is increased and wear powder is prevented from deviating. Can be achieved more reliably.

  Furthermore, in order to solve the above-described problem, the solid lubricated rolling bearing according to the present invention is configured to prevent or suppress scattering of abrasion powder of solid lubricant generated inside the solid lubricated rolling bearing to the outside of the bearing. Solid lubrication in which a fixed peripheral edge of an annular shield plate is attached to the shoulder of one of the rolling bearings, and the free peripheral edge of the shield plate is brought close to or in contact with the shoulder of the other bearing ring In the rolling bearing, it is possible to adopt a configuration in which a retaining portion for wear powder is formed by the cooperation of the shield plate and the race.

  The staying portion formed by the cooperation of the shield plate and the raceway has the following configuration.

(1) The shield plate is constituted by a metal outer peripheral member and an inner peripheral member made of a heat-resistant soft material integrated therewith, and the outer peripheral member is attached to the one race ring, and the inner peripheral member A structure in which the staying portion is formed inside the shield plate by sliding contact with a seal groove of the other bearing ring facing each other.

(2) An annular lid member facing the free peripheral edge of the shield plate over the seal groove of the opposite raceway and facing the axially outer surface of the free peripheral edge with a required axial clearance. The structure which forms the said retention part inside the said shield board and a cover member by providing in the shoulder part of the said bearing ring.

(3) A labyrinth structure is formed by bending the free peripheral edge inward in the axial direction, and facing the tip of the bent portion into a groove provided on the outer surface of the shoulder of the facing race, The structure which forms the said retention part inside a shield board and a labyrinth structure part.

(4) A configuration in which a recessed groove is provided in the bottom surface of the seal groove provided in the raceway, and wear powder is retained in the recessed portion.

  The shield plate can be formed of stainless steel, ferritic or austenitic, Fe-based superalloy, Co or Ni-based alloy, heat-resistant steel such as intermetallic compounds (FeAl, etc.), ceramics, but cost and rust. In consideration of ductility, SUS301 and 304 are more preferable.

  At least one of the inner ring, outer ring, and rolling element of the solid lubricated rolling bearing can be formed of bearing steel, ceramics, or the like. As the bearing steel, high carbon chrome bearing steel, carburized steel, heat resistant steel, stainless steel, alloy tool steel, high speed tool steel, chrome steel, chrome molybdenum steel and the like can be adopted. As the stainless steel, martensitic stainless steel or the like can be adopted. As the ceramic, silicon nitride, sialon, zirconia, silicon carbide, or the like can be used. Further, an appropriate hardened layer may be formed on the surface layer of the bearing component using stainless steel or bearing steel as a base material. As the hardened layer, carburizing, carbonitriding, nitriding layer or the like can be adopted.

  As described above, according to the present invention, the stay portion formed by the cooperation of the shield plate and the race ring or the stay portion provided in the shield plate itself with the abrasion powder of the solid lubricant generated inside the solid lubricant rolling bearing. By confining in, it is possible to prevent or suppress the scattering of the wear powder to the outside.

FIG. 1 is a partially omitted cross-sectional view of the solid lubricated rolling bearing of the first embodiment. FIG. 2 is a partially omitted cross-sectional view of the solid lubricated rolling bearing of the second embodiment. FIG. 3 is a partially omitted sectional view of a modification of the second embodiment. FIG. 4 is a partially omitted sectional view of the solid lubricated rolling bearing of the third embodiment. FIG. 5 is a partially omitted sectional view of a modification of the third embodiment. FIG. 6 is a partially omitted cross-sectional view of the solid lubricated rolling bearing of the fourth embodiment. FIG. 7 is a partially omitted cross-sectional view of the solid lubricated rolling bearing of the fifth embodiment. FIG. 8 is a partially omitted cross-sectional view of the solid lubricated rolling bearing of the sixth embodiment. FIG. 9 is a partially omitted step view of a modification of the sixth embodiment. FIG. 10 is a partially omitted step view of another modification of the sixth embodiment. FIG. 11 is a partially omitted cross-sectional view of the solid lubricated rolling bearing of the seventh embodiment. FIG. 12 is a partially omitted step view of the first modification of the seventh embodiment. FIG. 13 is a partially omitted step view of a second modification of the seventh embodiment. FIG. 14 is a partially omitted step view of the third modification of the seventh embodiment. FIG. 15 is a partially omitted step view of the fourth modification of the seventh embodiment. FIG. 16 is a partially omitted step view of the fifth modification of the seventh embodiment. FIG. 17 is a partially omitted step view of a sixth modification of the seventh embodiment. FIG. 18 is a partially omitted cross-sectional view of the solid lubricated rolling bearing of the eighth embodiment. FIG. 19 is a partially omitted sectional view of a conventional example.

Embodiments of the present invention will be described below with reference to the accompanying drawings.
[Embodiment 1]

  The rolling bearing 10 according to the first embodiment shown in FIG. 1 includes an outer ring 11 that is a fixed ring when in use, an inner ring 12 that faces the outer ring 11, and a large number of rolling elements interposed between the raceway grooves 13 and 14 of both. 15. It is comprised by the holder | retainer 16 which hold | maintains between each rolling element 15 at predetermined spacing.

  A mounting groove 18 is provided over the entire circumference of the shoulder 17 on both sides of the inner diameter surface of the outer ring 11, and a seal groove 21 is provided over the entire circumference of the shoulder 19 of the outer diameter surface of the inner ring 12 facing this. A shoulder outer peripheral edge 22 that is higher (larger radius) than the bottom surface of the seal groove 21 and lower (smaller radius) than the shoulder portion 19 is provided outside the seal groove 21 in the axial direction.

  Although not shown, the rolling bearing 10 is lubricated by a solid lubrication system, and a solid lubricant layer made of a solid lubricant or a composite containing the lubricant is provided on the contact surface of the cage 16 with the rolling element 15. It is done. As the solid lubricant, graphite, tungsten disulfide or molybdenum disulfide is used.

  The outer peripheral edge 24 (referred to as “fixed side peripheral edge” in the claims) of the shield plate 23 is fitted and fixed in the mounting groove 18. A portion continuous with the outer peripheral edge 24 is bent outward in the axial direction to form a bent portion 25. The bent portion 25 extends to the outside of the bearing width, and its tip is bent in the inner diameter direction to form an intermediate portion 26. A tip on the inner diameter side of the intermediate portion 26 is bent inward in the axial direction to form an inner peripheral edge 27 (referred to as “free-side peripheral edge” in the claims).

  The inner peripheral edge 27 reaches above the seal groove 21 via the shoulder outer peripheral edge 22 of the inner ring 12. A radial gap δ1 between the inner peripheral edge 27 and the shoulder outer peripheral edge 22 forms a labyrinth seal. The gap δ1 prevents the shield plate 23 from coming into contact with the inner ring 12, while preventing or suppressing foreign matter from entering from the outside or abrasion powder scattering from the inside to the outside.

  The bent portion 25, the intermediate portion 26, and the inner peripheral edge portion 27 form a circumferential groove 28 that protrudes outward from the bearing width toward the outside of the bearing. The circumferential groove 28 has a shape in which the intermediate portion 26 serves as a bottom surface and is open toward the bearing inward on the opposite side. The inside of the circumferential groove 28 becomes a wear powder retention part 29. The volume of the retention portion 29 is appropriately determined in consideration of the amount of solid lubricant used in the bearing.

  As the rolling bearing 10, a deep groove ball bearing is shown in the figure, but a double row angular ball bearing may be used. Moreover, although the outer ring 11 is a fixed-side track ring and the inner ring 12 is a rotation-side track ring in use, the opposite is also possible. In both cases of inner ring rotation and outer ring rotation, the shield plate 23 is fixed to the outer ring 11.

  The rolling bearing 10 of the first embodiment is as described above. When used as a bearing for a tenter clip, since the lubrication is a solid lubrication system, the lubrication action is hindered even at extremely high temperatures. There is nothing. Further, the abrasion powder of the solid lubricant generated during the operation of the bearing is received by the staying portion 29 and stays there. Further, it also stays in the portion of the seal groove 21.

  Although it is difficult to completely prevent the wear powder that escapes from the gap δ1 forming the labyrinth seal to the outside, the gap δ1 can be prevented or suppressed by sufficiently reducing the size of the gap δ1.

As described above, in the solid lubricated rolling bearing 10 of the first embodiment, most of the wear powder of the solid lubricant is retained in the retaining portion 29 inside the bearing and a part is retained in the seal groove 21, so Can be prevented or suppressed.
[Embodiment 2]

  The solid lubricated rolling bearing 10 according to the second embodiment shown in FIG. 2 has a circumferential groove 28 bent between the outer peripheral edge 24 and the inner peripheral edge 27 of the shield plate 23 as compared with the first embodiment. The bottom surface is within the width of the bearing and is formed shallower than the circumferential groove 28 of the first embodiment. A shallow folded portion 31 is provided at the tip of the inner peripheral edge 27 that is bent inward.

  The folded bent portion 31 faces the inclined surface 32 from the seal groove 21 of the inner ring 12 to the shoulder portion 19 with a small gap δ2. The gap δ2 forms a labyrinth seal together with the gap δ1.

  A circumferential groove 28 that extends over the entire circumference is formed by the bent portion 25, the intermediate portion 26, the inner peripheral edge portion 27, and the folded-back bent portion 31. By providing the folded-back bent portion 31, the volume of the staying portion 29 increases, and at the same time, the deviation of the wear powder remaining in the staying portion 29 is prevented or suppressed. Other configurations are the same as those in the first embodiment.

As shown in FIG. 3 as a modified example of FIG. 2, a fold-like folded bent portion 33 that is folded deeper at the tip of the folded bent portion 31 can be provided. Thereby, while being able to aim at the further increase in the volume of the retention part 29, the deviation of abrasion powder can be prevented or suppressed more effectively.
[Embodiment 3]

  In the third embodiment shown in FIG. 4, the configuration of the second embodiment is applied to the configuration of the first embodiment. That is, as in the first embodiment (see FIG. 1), the bent portion 25 of the shield plate 23 extends to the outside of the bearing width, and the inner peripheral edge portion 27 is bent greatly inward accordingly. As a result, the bottom surface of the circumferential groove 28 protrudes outward from the bearing width, and the volume of the staying portion 29 is increased. Further, similarly to the second embodiment (see FIG. 2), a folded back portion 31 that is shallowly folded is provided at the tip of the inner peripheral edge portion 27. Other configurations are the same as those in the first embodiment.

As in the modification shown in FIG. 5, a burly deep folded bent portion 33 can be provided at the tip of the folded bent portion 31. Similar to the case of FIG. 3, the volume of the retention portion 29 can be further increased, and the deviation of the wear powder can be more effectively prevented or suppressed.
[Embodiment 4]

  The shield plate 23 of the solid lubricated rolling bearing 10 of Embodiment 4 shown in FIG. 6 includes an outer peripheral member 34 made of metal such as iron and an inner peripheral member 35 made of a heat resistant soft material. The outer peripheral member 33 includes an outer peripheral edge portion 36 that is bent into a pipe shape and two sandwiching pieces 37 and 38 that face each other in the axial direction. The outer sandwiching piece 37 is formed continuously with the outer peripheral edge 36. The inner sandwich piece 38 is joined to another member by welding.

  Approximately half of the outer peripheral side of the inner peripheral member 35 is firmly sandwiched between the sandwiching pieces 37 and 38, and the outer peripheral member 34 and the inner peripheral member 35 are integrated. The inner peripheral side of the inner peripheral member 35 is brought into contact with an inclined surface 39 between the bottom surface of the seal groove 21 of the inner ring 12 and the outer peripheral edge 22 of the shoulder portion to constitute a contact type seal.

  As the heat resistant soft material constituting the inner peripheral member 35, for example, there is a fiber-based heat insulating material such as ceramic fiber excellent in heat resistance and sound absorption.

As described above, the shield plate 23 according to the fourth embodiment is constituted by the outer peripheral member 34 made of metal such as iron and the inner peripheral member 35 made of a heat-resistant soft material, and thus can be used at an extremely high temperature. Further, since the contact-type seal is configured by the cooperation of the shield plate 23 and the inner ring 12 in which the inner peripheral member 35 is slidably contacted, a staying portion 29 closed to the outside is formed. For this reason, the abrasion powder generated inside the bearing can be confined in the staying portion 29, and scattering to the outside can be surely prevented.
[Embodiment 5]

  The shield plate 23 of the fifth embodiment shown in FIG. 7 is fitted to the mounting groove 18 provided on the shoulder portion 17 of the outer ring 11 at the outer peripheral edge portion 24 in the same manner as the conventional example (see FIG. 18). Fixed. The inner peripheral edge 27 of the shield plate 23 is bent inward. The inner peripheral edge 27 faces the outer peripheral edge 22 of the outer diameter surface of the inner ring 12 with a predetermined radial gap δ3. The entire shield plate 23 is within the width of the bearing.

  In the conventional case, the circumferential groove 28 formed by the bent portion 25, the intermediate portion 26, and the inner peripheral edge portion 27 is shallow, and the presence of the gap δ3 (corresponding to the gap δ in FIG. 18) causes the abrasion powder to scatter. It was.

  On the other hand, in the case of the fifth embodiment, an annular lid member 41 is fitted and fixed to the outer peripheral edge 22 of the shoulder portion of the inner ring 12 outside the shield plate 23. The radial width of the lid member 41 is about half of the radial width of the shield plate 23 and is opposed to the shield plate 23 with a small gap δ3 in the axial direction. A labyrinth seal is formed by the gap δ3.

As described above, in the case of the fifth embodiment, the stay portion 29 having a required volume is configured by the cooperation of the shield plate 23, the lid member 41 attached to the inner ring 12 and the gap δ3 constituting the labyrinth seal. Wear powder generated inside the bearing is confined in the staying portion 29. By appropriately setting the size of the gap δ4, it is possible to prevent or suppress the scattering of wear powder to the outside.
[Embodiment 6]

  The shield plate 23 of the sixth embodiment shown in FIG. 8 is fitted to the mounting groove 18 provided on the shoulder portion 17 of the outer ring 11 at the outer peripheral edge portion 24 as in the above-described conventional example (see FIG. 18). Fixed. The inner peripheral edge 27 of the shield plate 23 is bent inward. The inner peripheral edge 27 faces the outer peripheral edge 22 of the outer diameter surface of the inner ring 12 with a predetermined radial gap δ3. The entire shield plate 23 is within the width of the bearing.

  In the conventional case (see FIG. 18), the circumferential groove is shallow and the presence of the gap δ causes the abrasion powder to be scattered. In the case of the sixth embodiment, the outer surface of the shoulder portion 19 of the inner ring 12 is used. The labyrinth groove 42 is provided, and the tip end portion of the inner peripheral edge portion 27 is inserted into the labyrinth groove 42 with a necessary gap in the radial direction and the circumferential direction.

  A gap represented by gaps δ5 and δ6 is formed between the tip of the inner peripheral edge 27 and the labyrinth groove 42. Further, since the gap δ3 described above exists between the inner peripheral edge portion 27 and the shoulder outer peripheral edge 22, a labyrinth seal is constituted by these gaps δ3, δ5, δ6, and the like.

  As described above, in the case of the sixth embodiment, the retention portion 29 having a required volume is formed by the cooperation of the shield plate 23 and the labyrinth seals with the gaps δ3, δ5, δ6, etc. on the inner ring 12 side, and is generated inside the bearing. The worn wear powder is trapped in the staying portion 29. By appropriately setting the sizes of the gaps δ3, δ5, δ6, etc., it is possible to prevent or suppress the scattering of wear powder to the outside.

  The modification shown in FIG. 9 is the one shown in FIG. 8 in which the bottom surface of the circumferential groove 28 is deeply formed so as to protrude outward of the bearing width (see FIG. 1), and the volume of the staying portion 29 is further increased. It has become.

In another modification shown in FIG. 10, in the case of FIG. 8, an annular lid member 41 is fitted and fixed to the outer peripheral edge 22 of the shoulder portion of the inner ring 12 (see FIG. 7). The width in the radial direction of the lid member 41 is about half the radial width of the shield plate 23, and is opposed to the shield plate 23 with a small gap δ 4 in the axial direction. A labyrinth seal is formed by the gap δ4. Compared to the case of FIG. 8, the gap δ4 is increased, so that the effect of the labyrinth seal is increased.
[Embodiment 7]

  The solid lubricated rolling bearing 10 of the seventh embodiment shown in FIG. 11 is the same as that of the conventional example (see FIG. 18) except for the shape of the seal groove 21 of the inner ring 12 and the other parts including the shield plate 23. It is.

  In the case of the seventh embodiment, a recessed groove 43 that is recessed deeper into the bottom surface of the seal groove 21 is provided. The shield plate 23 is fitted and fixed to the mounting groove 18 provided on the shoulder portion 17 of the outer ring 11 at the outer peripheral edge portion 24 in the same manner as in the conventional example (see FIG. 18). The inner peripheral edge 27 of the shield plate 23 is bent inward. The inner peripheral edge 27 faces the outer peripheral edge 22 of the outer diameter surface of the inner ring 12 with a predetermined radial gap δ3. The entire shield plate 23 is within the width of the bearing.

  In the case of the seventh embodiment, since the concave groove 43 described above is provided on the bottom surface of the seal groove 21, the wear powder moved from the inside of the bearing to the shield plate 23 side falls into the concave groove 43 and stays there. The wear powder that has not dropped is restricted from being scattered to the outside by a labyrinth seal having a clearance δ3.

  A portion including the recessed groove 43 inside the shield plate 23 and the gap δ 3 becomes the staying portion 29, and a wear portion generated inside the bearing is confined in the staying portion 29 including the recessed groove 43. Thereby, scattering of the wear powder to the outside can be suppressed.

  12 to 17 are modifications of the seventh embodiment shown in FIG. 11, and the following configuration is applied based on the configuration of FIG.

12 shows the configuration of FIG. 1, FIG. 13 shows the configuration of FIG. 4, FIG. 14 shows the configuration of FIG. 4, FIG. 14 shows the configuration of FIG. 5, and FIG. Modification 4 applies the configuration of FIG. 6, Modification 5 shown in FIG. 16 applies the configuration of FIG. 7, and Modification 6 shown in FIG. 17 applies the configuration of FIG. In either case, both configurations have the same effect.
[Embodiment 8]

  The embodiment shown in FIG. 18 is a rolling bearing in which a plurality of rolling elements are arranged between inner and outer rings, and a plurality of separators 44 formed by a solid lubricant are interposed between the rolling elements in the circumferential direction. The lubricant is gradually supplied to the raceway surface by the separator 44 formed by the above. A strip 45 having a width smaller than the circumferential width of the separator 44 is integrated with at least one of the opposing surfaces of the inner and outer rings excluding the circumferential surface in contact with the rolling elements 15 among the outer surfaces of the separator 44. . By providing the band 45, the rolling element 15 can be prevented from falling off from the inner and outer rings even if the separator 44 is worn.

  The shield plate 23 in each of the above embodiments may be formed of stainless steel, heat-resistant steel such as ferritic or austenitic, Fe-based superalloy, Co or Ni-based alloy, intermetallic compound (FeAl, etc.), or ceramics. However, in consideration of cost, rust, ductility, etc., SUS301 and 304 are more preferable.

  In addition, at least one of the inner ring 12, the outer ring 11, and the rolling element 15 of the solid lubricated rolling bearing 10 can be formed of bearing steel, ceramics, or the like. As the bearing steel, high carbon chrome bearing steel, carburized steel, heat resistant steel, stainless steel, alloy tool steel, high speed tool steel, chrome steel, chrome molybdenum steel and the like can be adopted. As the stainless steel, martensitic stainless steel or the like can be adopted. As the ceramic, silicon nitride, sialon, zirconia, silicon carbide, or the like can be used. Further, an appropriate hardened layer may be formed on the surface layer of the bearing component using stainless steel or bearing steel as a base material. As the hardened layer, carburizing, carbonitriding, nitriding layer or the like can be adopted.

δ1 to δ6 Clearance 10 Rolling bearing 11 Outer ring 12 Inner ring 13, 14 Race groove 15 Rolling body 16 Retainer 17 Shoulder 18 Mounting groove 19 Shoulder 21 Seal groove 22 Shoulder outer peripheral edge 23 Shield plate 24 Outer peripheral edge 25 Bent part 26 Intermediate portion 27 Inner peripheral edge 28 Circumferential groove 29 Staying portion 31 Folded bent portion 32 Inclined surface 33 Folded bent portion 34 Outer peripheral member 35 Inner peripheral member 36 Outer peripheral edge portion 37, 38 Clamping piece 39 Inclined surface 41 Lid member 42 Labyrinth groove 43 Recessed groove 44 Separator 45 Band

Claims (10)

  In order to prevent or suppress the solid lubricant wear powder generated inside the solid lubricated rolling bearing from scattering outside the bearing, the fixed side of the annular shield plate on the shoulder of one of the bearing rings of the rolling bearing In a solid lubricated rolling bearing in which a peripheral edge is attached and the free-side peripheral edge of the shield plate is brought close to or in contact with the shoulder of the other race ring, the portion between the fixed-side peripheral edge and the free-side peripheral edge of the shield plate A solid-lubricated rolling bearing characterized in that a circumferential groove opened toward the inside of the bearing by bending is formed, and a retaining portion for wear powder is formed by the circumferential groove.   A shallow folded bent portion is provided at a tip of a free-side peripheral edge portion that is bent inward to form the peripheral groove, and a stay portion for wear powder is formed by the peripheral groove including the bent portion. The solid lubricated rolling bearing as described in 1.   The solid-lubricated rolling bearing according to claim 2, wherein a folded portion that is folded deeper is provided at a tip of the folded portion.   In order to prevent or suppress the solid lubricant wear powder generated inside the solid lubricated rolling bearing from scattering outside the bearing, the fixed side of the annular shield plate on the shoulder of one of the bearing rings of the rolling bearing In a solid lubricated rolling bearing in which a peripheral edge is attached and the free peripheral edge of the shield plate is brought close to or in contact with the shoulder of the other race ring, a stay portion for wear powder is formed by the cooperation of the shield plate and the race ring. Solid lubricated rolling bearing characterized by the above.   The structure of the stay portion formed by the cooperation of the shield plate and the raceway is configured by forming the shield plate with a metal outer peripheral member and an inner peripheral member made of a heat-resistant soft material integrated therewith, The outer peripheral member is attached to the one bearing ring, and the staying portion is formed inside the shield plate by sliding the inner peripheral member into a seal groove of the other bearing ring facing the outer ring member. The solid-lubricated rolling bearing according to claim 4,   The structure of the stay portion formed by the cooperation of the shield plate and the raceway ring is such that the free side peripheral edge portion of the shield plate faces the seal groove of the opposite raceway ring, and the axial side outer surface of the free side peripheral edge portion. It is a configuration in which the staying portion is formed inside the shield plate and the lid member by providing an annular lid member facing the gap in the required axial direction on the shoulder of the raceway ring. The solid lubricated rolling bearing according to claim 4.   The structure of the stay portion formed by the cooperation of the shield plate and the raceway is such that the free side peripheral edge is bent inward in the axial direction, and the tip of the bend is opposed to the shoulder outer surface of the raceway. The solid lubricated rolling bearing according to claim 4, wherein a labyrinth structure is formed by facing the provided groove, and the staying portion is formed inside the shield plate and the labyrinth structure portion.   The structure of the stay portion formed by the cooperation of the shield plate and the raceway is provided with a recessed groove on the bottom surface of the seal groove provided on the raceway, and the shield plate and the outer peripheral edge of the shoulder portion of the raceway The solid lubricated rolling bearing according to claim 4, wherein a labyrinth seal is provided between the shield plate and the stay portion is formed by a portion including the concave groove inside the shield plate and the labyrinth seal. .   The labyrinth seal is formed by bending the free peripheral edge inward in the axial direction and facing the labyrinth groove provided on the shoulder outer surface of the opposed race ring. The solid-lubricated rolling bearing according to claim 8. The solid lubricated rolling bearing according to any one of claims 1 to 9, wherein the rolling bearing is either a deep groove ball bearing or a double row angular ball bearing.

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