JP2009133418A - Rolling bearing - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a rolling bearing superior in economic efficiency, by improving the service life of the rolling bearing by delaying an advance speed of fretting. <P>SOLUTION: This rolling bearing has an inner ring member 1 having a rolling groove 11 on an outside surface 1B, an outer ring member 2 having a rolling groove 21 on an inside surface 2A, and a rolling element 3 rolling on these rolling grooves 11 and 21, and is formed by sealing a lubricant 6 between the inner ring member 1 and the outer ring member 2. The rolling bearing is characterized in that the inner ring member 1 has a micropore H communicating with the inside surface 1A from the outside surface 1B, and the inside surface 1A is formed with an abraded recessed place 12 for not contacting with a shaft member 8 fitted to the inner ring member 1 by clearance fit. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to a structure that maintains the lubrication performance of a rolling bearing such as a ball bearing or a roller bearing, particularly a rolling bearing having a gap fitting structure.

  From the old days to the present, bearings are used in the rotating parts of various devices in many fields. Bearing life and frictional resistance greatly affect the life and quality of equipment, so use lubricants to improve the life of bearings or reduce frictional resistance and maintain lubrication performance for a long period of time. Has been done in various ways. As a representative bearing, a sintered oil-impregnated bearing in which a lubricating oil is soaked in a porous sintered metal has been proposed, and is actually widely used as a sliding bearing (see, for example, Patent Document 1). In addition, a sliding bearing (see, for example, Patent Document 2) is also disclosed in which an oil reservoir is provided in the bearing, pores are drilled, and lubricating oil in the oil reservoir is supplied to the shaft member surface through the drilled pores.

  Furthermore, the cage is made of sintered metal and oil-impregnated to improve lubricity (for example, see Patent Document 3), or all of the balls as rolling elements or a small diameter for imparting lubricity. A rolling bearing in which a non-load ball is formed of a sintered metal and oil-impregnated to improve lubricity (for example, see Patent Documents 4 and 5), at least one of an inner ring member or an outer ring member is composed of a sintered metal, Rolling bearings with improved lubricity (for example, see Patent Document 6), rolling bearings that form through holes in the inner ring member and supply lubricating oil into the bearings from the shaft member side through the through holes (for example, Patent Documents) 7) or a rolling bearing (for example, see Patent Document 8) that forms a through hole in the outer ring member and supplies lubricating oil into the bearing through the through hole from the housing side located outside the outer ring member. To have.

Bearings using sintered metal are not limited to the above-mentioned patent documents, and are intended to contain lubricating oil. The lubricating oil is pre-absorbed in a cage, ball, outer ring member or inner ring member made of sintered metal. By keeping it in place, the lubrication performance between the rolling elements and the rolling surfaces is improved and maintained. In rolling bearings that do not use sintered metal, a lubricant is generally enclosed in the bearing in order to improve lubrication performance. However, this is described in Patent Documents 7 and 8 cited above. As described above, there is a structure in which lubricating oil is supplied from the housing or the shaft member into the bearing through the pores provided in the outer ring member or the inner ring member.
JP-A-5-10331 JP-A-6-147227 JP-A-7-259867 JP 11-62975 A JP 2005-133881 A JP-A-9-25938 JP 2001-99166 A JP 2005-98467 A

  When the rolling bearing is attached to the shaft member, the shaft member is generally press-fitted into the inner ring member of the rolling bearing and fixed firmly. When the outer ring member of the rolling bearing is attached to an attachment member such as a device, the outer ring member or the housing of the rolling bearing is generally press-fitted into the attachment member and firmly fixed. In this way, when firmly fixed by press-fitting, there is no relative minute movement between the inner ring member and the shaft member or between the outer ring member and the mounting member such as equipment, so it is known as fretting. No damage will occur. Therefore, when the rolling bearing is firmly fixed by press-fitting, it is only necessary to consider improvement and maintenance of the lubricating performance between the rolling elements and the rolling surface.

  However, the frequency of use of OA equipment, such as a printer that is a terminal device of a computer, has increased dramatically, and it may be necessary to maintain and replace the rolling bearing in the middle. In order to facilitate the maintenance and replacement of this rolling bearing, there are an increasing number of cases in which the rolling bearing is not fitted to a shaft member or the like by press-fitting but fitted into a gap. For example, if the shaft member is fitted into the inner ring member with a gap, micro vibrations and micro oscillations are repeatedly performed on the contact surface between the inner ring member and the shaft member during operation of the device, that is, during rotation of the shaft member. Oxidation and wear at these abutting surfaces proceed and damage called fretting occurs. In the case of clearance fitting, fretting cannot be avoided, and this fretting shortens the life of the rolling bearing and increases the number of maintenance.

  In the present invention, when a rolling bearing is mounted on a shaft or a mounting member of a device with a clearance fit, the service life can be sufficiently improved by greatly delaying the fretting speed and manufactured with a simple structure. The main object is to provide a rolling bearing that is easy to do.

  1st invention is equipped with the inner ring member which has a rolling groove in an outer surface, the outer ring member which has a rolling groove in an inner surface, and the rolling element which rolls these rolling grooves, The said inner ring member and the said outer ring In a rolling bearing in which a lubricant is sealed between the inner ring member and the inner ring member, the inner ring member has a minute hole communicating from the outer surface to the inner surface. There is provided a rolling bearing characterized in that a non-wear recess is formed so as not to contact a shaft member.

  2nd invention is provided with the inner ring member which has a rolling groove in an outer surface, the outer ring member which has a rolling groove in an inner surface, and the rolling element which rolls these rolling grooves, The said inner ring member and the said outer ring In a rolling bearing in which a lubricant is sealed between the outer ring member and the outer ring member, the outer ring member has a minute hole communicating from the inner side surface to the outer side surface. The present invention provides a rolling bearing characterized in that a non-wear recess is formed so as not to contact the mounting member.

  According to a third aspect of the present invention, there is provided an inner ring member having a rolling groove on the outer surface, an outer ring member having a rolling groove on the inner surface, a rolling element that rolls the rolling groove, and a gap between the inner surface of the inner ring member. A rolling bearing formed by sealing a lubricant between the inner ring member and the outer ring member, and the inner ring member has a fine hole communicating from the outer surface to the inner surface. A rolling bearing is provided in which a non-wear recess is formed in a surface of the shaft member that faces the inner ring member so as not to contact the inner side surface of the inner ring member.

  According to a fourth aspect of the present invention, there is provided an inner ring member having a rolling groove on the outer surface, an outer ring member having a rolling groove on the inner surface, a rolling element that rolls the rolling groove, and a gap between the outer surface of the outer ring member and the outer ring member. A rolling bearing formed by sealing a lubricant between the inner ring member and the outer ring member, and the outer ring member has a fine hole that communicates from the inner side surface to the outer side surface. A rolling bearing is provided in which a non-wearing recess for preventing contact with the outer surface of the outer ring member is formed on a surface of the mounting member facing the outer ring member.

  According to a fifth invention, in any one of the first invention to the fourth invention, a surface on which the rolling groove is formed is smoothed by polishing or grinding, and other than the rolling groove in the inner ring member The outer surface of the outer ring member or at least a part of the inner surface other than the rolling groove in the outer ring member is not polished or ground, and the fine holes are not blocked by the polishing or grinding. A rolling bearing is provided.

  According to a sixth aspect of the present invention, in any one of the first to fifth aspects, the non-abrasion on the facing surface between the inner ring member and the shaft member or the facing surface between the outer ring member and the mounting member. There is provided a rolling bearing characterized in that a ratio of a surface area in which a recess is formed and a surface area in which the non-wear recess is not formed is in a range of 0.2 to 1.0.

  According to the first aspect of the present invention, the lubricant oil existing on the outer surface side of the inner ring member is oozed into the inner surface side by the fine-diameter through holes (micro holes) formed in the inner ring member made of the porous material. In addition to improving the lubrication performance of the contact surface between the inner surface of the inner ring member and the shaft member, the inner surface of the inner ring member has a non-wear recess, so that the contact surface between the inner ring member and the shaft member Even if the micropores are blocked by the metal particles generated by fretting due to the relative micromotion of the micropores, the micropores that lead to the non-wearing recesses are not blocked, and the lubricating oil oozes out, so the fretting speed is greatly delayed. Therefore, the life of the rolling bearing can be greatly improved. Moreover, since the lubricating oil is oozed out using the fine holes formed in the porous material, there is no need for a step of drilling through holes separately, and when the rolling holes are polished, etc. By adjusting the width of the surface area where polishing or the like is performed together, the amount of oil that oozes out to the contact surface between the inner surface of the inner ring member and the shaft member can be adjusted. Therefore, it is possible to provide a rolling bearing that is easy to manufacture, inexpensive, has no leakage of lubricating oil, and has a significantly improved life. The first invention is particularly suitable when the inner ring member and the shaft member are fitted into a gap.

  According to the second aspect of the present invention, the lubricant oil existing on the inner surface side of the outer ring member is oozed to the outer surface side by the fine diameter through-holes (micro holes) formed in the outer ring member made of the porous material. In addition to improving the lubrication performance of the contact surface between the outer surface of the outer ring member and the mounting member, the outer surface of the outer ring member has a non-wear recess, so that the contact surface between the outer ring member and the mounting member Even if the fine holes on the abutment surface are blocked by the metal particles generated by fretting due to relative micro-movements, the lubricating oil oozes out from the fine holes leading to the non-wear recesses, greatly increasing the fretting speed. As in the first aspect of the invention, it is possible to provide a rolling bearing that is easy to manufacture, inexpensive, has no leakage of lubricating oil, and has a significantly improved life. The second aspect of the invention is particularly suitable when the outer ring member and the attachment member are fitted into a gap.

  According to the third invention, the inner ring member made of a porous material is not formed with a non-wear recess, but the shaft member is provided with a non-wear recess on the surface facing the inner ring member. Even if the micropores are blocked by the metal particles generated by fretting due to the relative micromotion of the contact surface with the shaft member, the lubricating oil oozes out from the micropores that lead to the non-wear recess. The same effects as the invention can be achieved.

  According to the fourth aspect of the invention, the outer ring member made of the porous material is not formed with the non-wear recess, but the non-wear recess is provided on the opposing surface of the mounting member that faces the outer ring member. Even if the fine holes in the contact surface are blocked by the metal particles generated by fretting due to the relative minute movement of the contact surface with the mounting member, the lubricating oil oozes out from the micro holes leading to the non-wear recess. The same effects as those of the second invention can be obtained.

  According to the fifth aspect of the invention, in addition to the effects of the first to fourth aspects of the invention, the rolling elements are rolled by polishing the rolling grooves of the inner ring member or the outer ring member made of a porous material. Since the friction is reduced and at least a part of the surface of the inner ring member or the outer ring member other than the rolling groove is not polished, an appropriate amount of lubricating oil can be oozed out to the contact surface, and therefore the lubrication performance is increased. Since the period can be maintained, not only the quality of the rolling bearing can be improved, but also the life can be improved.

  According to the sixth aspect of the invention, the surface area where the non-wear recess is formed on the facing surface between the inner ring member and the shaft member or the facing surface between the outer ring member and the mounting member, and the non-wear recess. Since the ratio of the surface area where no place is formed is in the range of 0.2 to 1.0, the effects of the first to fifth inventions can be further improved.

[Embodiment 1]
A rolling bearing according to a first embodiment of the present invention will be described with reference to FIGS. FIG. 1 is a view for explaining the outline of the rolling bearing of the present invention. FIG. 2 is a view for explaining an inner ring member of the rolling bearing, and FIGS. 2A and 2B are views for explaining a cross section (hatched lines are omitted) of the inner ring member. The rolling bearing includes an inner ring member 1, an outer ring member 2, a rolling element 3 (in the first embodiment, a ball such as a steel ball is used, hereinafter referred to as a ball), and a cage 4 for holding the ball 3. The pair of shield members 5 closes the gap between the inner ring member 1 and the outer ring member 2 at both ends, and a lubricant 6 is sealed in the gap between the inner ring member 1 and the outer ring member 2.

  The outer surface 2B of the outer ring member 2 is fitted into the mounting surface 7A of the mounting member 7 with a gap. The attachment member 7 is, for example, a fixing member for a device (not shown). A columnar or cylindrical shaft member 8 is attached to the inner ring member 1 with a clearance fit. Therefore, replacement and maintenance of this rolling bearing can be performed easily. In the first embodiment, the shaft member 8 does not have to be a single component constituting a rolling bearing. When the mounting member 7 is a rolling bearing housing, the outer ring member 2 is press-fitted into the mounting member 7, and the mounting member 7 is fixed to a device (not shown) or the like by simple fixing means such as screwing.

  The inner ring member 1 is made of a porous material such as a sintered metal or a metal injection mold (MIM) material. The metal injection mold material is obtained by kneading metal powder and a resin binder, injection molding, removing the resin binder by heat treatment, and sintering the metal alone. Sintered metal is widely known compared to metal injection molding materials, so the explanation is omitted. Porous materials such as sintered metals and metal injection mold materials have minute spaces formed between countless metal particles and metal particles, and fine holes are formed by the minute spaces. Accordingly, the inner ring member 1 made of a porous material is formed with a plurality of fine through-holes (hereinafter referred to as “micropores”) H extending from the narrow inner surface 1A to the outer surface 1B. Unlike the straight through-holes drilled by an electron beam or laser light, the micro-holes H are winding, and are micro holes with a diameter of about 2 μm to 20 μm on average.

  A rolling groove 11 on which the ball 3 rolls is generally formed on the outer surface 1B of the inner ring member 1 by polishing or grinding. The rolling groove 11 has a general shape of a deep groove type, but because of the porous material, the rolling groove 11 and the rolling groove of the outer ring member 2 are obtained by finishing the rolling groove 11 by polishing or the like. The rolling friction resistance when the ball 3 rolls 21 can be reduced. Even when the rolling groove 11 is formed during pressure molding, the groove wall is polished and smoothed. The groove wall forming the rolling groove 11 by a machining process such as polishing is a smooth surface, but the fine holes H in the surface area of the rolling groove 11 are clogged and blocked by metal particles generated during the grinding process. It will come off. However, since a part of the outer surface 1B of the inner ring member 1 excluding the groove wall that forms the rolling groove 11 is not polished, the fine holes H communicating with the outer surface 1B of the inner ring member 1 are not blocked. Accordingly, the oil of the lubricant 6 oozes out to the contact surface between the inner side surface 1A of the inner ring member 1 and the shaft member 8 through the minute hole H that communicates from the outer side surface 1B except the rolling groove 11 to the inner side surface 1A. That is, the fine hole H guides the oil of the lubricant 6 to the inner surface 1 </ b> A of the inner ring member 1.

  In general, in the case of sintered metal, the diameter of the fine hole H is determined by main conditions such as the diameter of the metal particles and the pressure applied during the production. In the case of injection molding, the metal particles and the resin particles The diameter of the fine hole H is determined depending on the main conditions such as the mixing ratio and the diameter of the metal particles and the pressure applied during molding. Therefore, by selecting these production conditions, it is possible to produce a porous material with micropores H having an appropriate pore diameter. However, if the amount of lubricating oil that oozes through the micropores H is large, rolling By polishing a part of the outer surface 1B of the inner ring member 1 excluding the groove wall forming the groove 11, the amount of oil that oozes out through the fine hole H can be adjusted.

  Thus, since the oil of the lubricant 6 oozes out through the fine holes H to the contact surface between the inner surface 1A of the inner ring member 1 and the shaft member 8, the fretting speed is slowed and the life is improved. During the rotation of the shaft member 8, minute vibrations and minute fluctuations occur regardless of the presence or absence of lubricating oil. The presence of lubricating oil on the contact surface between the inner surface 1A of the inner ring member 1 and the shaft member 8 slows the fretting speed. However, fretting occurs over a long period of time, and the metal particles generated by the fretting are fine. The hole H is clogged, and the lubricating oil does not ooze out from the fine hole H. Then, if the lubricating oil does not exist on the contact surface between the inner surface 1A of the inner ring member 1 and the shaft member 8, the fretting speed increases, which adversely affects the lifespan.

  In order to solve this problem, as shown in FIG. 2A, in the first embodiment, a non-wear recess 12 that does not contact the shaft member 8 is formed on the inner side surface 1A of the inner ring member 1, and the inner ring member 1 is formed. The fine holes H extending from the outer surface 1B to the non-wear recess 12 are prevented from being clogged with metal particles generated by fretting. That is, even if the fine hole H leading to the inner side surface 1A of the inner ring member 1 excluding the non-wear recess 12 is blocked by clogging due to wear and does not ooze out the lubricating oil, the non-wear recess 12 of the inner ring member 1 is prevented. Since it does not contact with the shaft member 8 and does not wear and does not clog, the lubricating oil continues to ooze out from the fine holes H leading to the non-wear recess 12. Therefore, the lubrication performance of the contact surface between the inner surface 1A of the inner ring member 1 and the shaft member 8 is maintained with almost no change, and the life is further improved. In FIG. 2 (A), the non-wear recess 12 extends in the direction of the width W of the inner ring member 1, but an annular recess, or a striped recess having an annular recess intermittently, the width W The shape of the recess, such as a recess formed obliquely with respect to the direction, is arbitrary. Note that the non-wear recess 12 is formed simultaneously with the pressure molding of the inner ring member 1.

  Since the inner surface 1A of the inner ring member 1 and the shaft member 8 are coupled with a clearance fit, when the shaft member 8 rotates, as described above, the inner surface 1A of the inner ring member 1, the shaft member 8 and the contact surface Then, since minute vibrations and minute oscillations exist, and since the amount of lubricating oil that oozes out from the minute holes H communicating with the non-wear recess 12 is very small, the lubricant does not accumulate in the non-wear recess 12. Rather, a thin oil film is formed on the contact surface between the inner surface 1A of the inner ring member 1 and the shaft member 8 to maintain lubrication performance. Also from this, the non-wear recess 12 is for forming a non-contact portion that does not contact the shaft member 8 unlike the conventional oil sump, and the lubricating oil substantially accumulates in the non-wear recess 12. There is nothing.

  It is preferable that the surface area of the inner surface 1A excluding the surface area of the non-wear recess 12 and the surface area of the non-wear recess 12 are substantially equal, but may be in the range of about 0.2 to 1.0. When the ratio of the surface area of the non-wear recess 12 to the surface area of the inner face 1A excluding the non-wear recess 12 is less than about 0.2, the inner surface 1A of the inner ring member 1 excluding the non-wear recess 12 is communicated. From the stage where the fine holes H are clogged, the amount of lubricating oil that oozes out becomes too small, which is not preferable because the lubricating performance deteriorates. Further, when the ratio of the surface area of the non-wear recess 12 to the surface area of the inner face 1A excluding the non-wear recess 12 exceeds 1.0, the per unit area of the inner surface 1A excluding the non-wear recess 12 Since the load increases, the effect of reducing fretting is reduced, and the expected life cannot be obtained.

  In addition, since the outer ring member 2, the ball 3, the cage 4, and the shield member 5 are general ones, description thereof is omitted. As described above, the rolling bearing of the first embodiment uses the inner ring member 1 made of a porous material, and at least a part of the outer side surface 1B excluding the rolling groove of the inner ring member 1 is not polished and formed on the inner side surface 1A. Since the non-wear recess is formed, the structure is particularly suitable for the case where the shaft member 8 is fixed to the inner ring member 1 by a clearance fit, and the inner ring member 1 and the shaft member 8 are in contact with each other during the rotation of the shaft member 8. Even if relative minute movement occurs on the contact surface, the fretting speed is significantly reduced compared to the conventional case, so that the life can be improved. Of course, the inner ring member 1 may be pre-oiled.

[Embodiment 2]
The rolling bearing of the second embodiment will be described with reference to FIGS. 1 and 3. FIG. 3 is a view for explaining the outer ring member. In FIG. 3, the same symbols as those used in FIGS. 1 and 2 indicate members having the same names. The rolling bearing according to the second embodiment has the same structure as that shown in FIG. 1 and is a rolling bearing in which the outer side surface 2B of the outer ring member 2 is fitted into the mounting surface 7A of the mounting member 7 with a gap. The second embodiment is suitable for a rolling bearing in which the attachment member 7 rotates and the shaft member 8 is used in a fixed form.

  The inner ring member 1 of this rolling bearing is made of a general metal material made of steel or the like, and need not be made of a porous material. In the second embodiment, the inner ring member 1 is firmly fixed to the shaft member 8 by press fitting, and the shaft member 8 is a member constituting this rolling bearing. In the second embodiment, a ball is used as the rolling element 3, so the rolling element is referred to as a ball 3. Since the balls 3, the cage 4, and the shield member 5 may be general ones, description thereof is omitted. The outer ring member 2 is made of a porous material such as a sintered metal or a metal injection mold material used to form the inner ring member 1 of the first embodiment.

  Similar to the inner ring member 1 of the first embodiment, the outer ring member 2 is formed with a minute hole H leading from the inner side surface 2A to the outer side surface 2B. A rolling groove 21 smoothed by polishing or the like is formed at substantially the center of the inner side surface 2A of the outer ring member 2. The rolling friction when the ball 3 rolls on the groove wall of the rolling groove 21 is reduced by this polishing process or the like, but the fine hole H that leads to the groove wall forming the rolling groove 21 by the metal particles generated in the process is reduced. Is clogged and the fine holes H are blocked, so that the oil of the lubricant 6 does not ooze into the fine holes H communicating with the groove walls forming the rolling grooves 21.

  For this reason, at least a part of the inner surface 2A excluding the groove wall of the rolling groove 21 in the outer ring member 2 is not polished or the like. The oil of the lubricant 6 soaks into the fine holes H leading to the unpolished surface area of the inner surface 2A, and oozes out to the outer surface 2B of the outer ring member 2 after a certain time. Due to the lubricating oil that oozes out, the lubrication performance of the contact surface between the outer surface 2B of the outer ring member 2 and the mounting member 7 is maintained in a good state, and the life of the rolling bearing is improved.

  Even if the lubrication performance of the contact surface between the outer surface 2B of the outer ring member 2 and the mounting member 7 is maintained in a good state, the shaft member 8 is press-fitted into the inner ring member 1, and the outer ring member 2 and the mounting member 7 Therefore, when the mounting member 7 rotates, a relative minute movement naturally occurs on the contact surface between the outer surface 2B of the outer ring member 2 and the mounting member 7 when the mounting member 7 rotates. Although the above-described fretting speed is slowed by maintaining the lubricating performance, fretting is unavoidable. For a long time, the metal particles generated by fretting clog the fine holes H communicating with the outer surface 2B of the outer ring member 2 and block them. If the fine holes H are blocked, the lubricating oil cannot ooze out to the outer surface 2B, the lubricating performance is lowered, and the fretting speed is increased, so that the improvement of the bearing life is suppressed.

  Therefore, in the second embodiment, the non-wear recess 22 is provided on the outer surface 2B of the outer ring member 2 fitted into the attachment member 7 so that the minute hole H leading from the inner surface 2A of the outer ring member 2 to the non-wear recess 22 is formed. I try not to cause clogging. That is, the outer surface 2B of the outer ring member 2 is not worn because only the non-wear recess 22 is not in contact with the mounting member 7, and a fine hole H leading to the outer surface 2B other than the non-wear recess 22 is generated by wear. Even after clogging with the metal particles, the fine holes H communicating with the non-wear recess 22 continue to ooze out the lubricating oil to the outer surface 2B without clogging, and maintain the lubricating performance. The non-wear recess 22 is formed together when the outer ring member 2 is pressure-molded.

  Here, as described above, the contact surface between the outer surface 2B of the outer ring member 2 and the mounting member 7 has a relative minute motion such as a minute vibration or a minute swing, and the non-wear recess 22 Since the amount of the lubricating oil that oozes out from the fine hole H that communicates is very small, the lubricating oil does not collect in the non-wear recess 22 and the contact between the outer surface 2B of the outer ring member 2 and the mounting surface 7A of the mounting member 7 does not occur. A thin oil film is formed on the contact surface to maintain lubrication performance. Also from this, the non-wear recess 22 is for forming a non-contact portion that does not contact the mounting member 7 unlike the conventional oil sump, and the lubricating oil substantially accumulates in the non-wear recess 12. And there is no leakage of lubricating oil.

  From such a viewpoint, it is preferable that the surface area of the outer surface 2B excluding the surface area of the non-wear recess 12 and the surface area of the non-wear recess 22 are substantially equal, but the ratio thereof is 0.2 to 1. It may be in the range of about. When the ratio of the surface area of the non-wear recess 22 to the surface area of the outer face 2B excluding the non-wear recess 22 is smaller than about 0.2, the outer surface 2B of the outer ring member 2 excluding the non-wear recess 22 is communicated. From the stage where the fine holes H are clogged, the amount of lubricating oil that oozes out becomes too small and the lubricating performance is lowered, which is not preferable. Further, when the ratio of the surface area of the non-wear recess 22 to the surface area of the outer face 2B excluding the non-wear recess 22 exceeds 1.0, the load per unit area applied to the outer surface 2B excluding the non-wear recess 22 Therefore, the effect of reducing fretting is reduced and the expected life cannot be obtained.

[Embodiment 3]
Embodiment 3 will be described with reference to FIG. FIG. 4 is an enlarged view of the vicinity of the contact surface between the inner ring member 1 and the shaft member 8, and the cross section is not hatched. In this embodiment, the shaft member 8 is fitted into the inner surface 1A of the inner ring member 1 with a gap. In the first embodiment, the non-wear recess 12 is provided on the inner side surface 1A of the inner ring member 1 into which the shaft member 8 is fitted with a clearance. In the third embodiment, the shaft member 8 facing the inner side surface 1A of the inner ring member 1 is provided. A non-wear recess 82 is formed on a surface (hereinafter referred to as an opposing surface) 81. The inner ring member 1 is made of the porous material as described above, and the non-wear recess 82 is formed on the facing surface 81 of the shaft member 8 without forming the above-mentioned non-wear recess on the inner surface 1A of the inner ring member 1. Since the structure is different from that of the first embodiment and the other parts are the same as those of the first embodiment, this different point will be described.

  The non-wear recess 82 formed on the opposed surface 81 of the shaft member 8 may be formed in the same shape and arrangement as those in which the non-wear recess 12 is formed on the inner side surface 1A of the inner ring member 1 in the first embodiment. According to this structure, the fine hole H that communicates with the inner surface 1A of the inner ring member 1 that contacts the facing surface 81 excluding the non-wear recess 82 of the shaft member 8 is blocked by the metal particles generated by fretting. The non-wearing recess 82 of the shaft member 8 does not come into contact with the inner side surface 1A of the inner ring member 1 and the surface area of the inner side surface 1A of the inner ring member 1 that does not come into contact does not wear. The fine holes H communicating with the surface area of the inner surface 1A facing the non-wear recess 82 of the member 8 continue to ooze out the lubricating oil. The oozed lubricating oil spreads on the opposing surface 81 of the shaft member 8 due to the relative minute movement generated by the rotation of the shaft member 8, and the lubricating performance is maintained in the same manner as in the first embodiment, so the life is greatly increased. Can be improved.

[Embodiment 4]
Embodiment 4 will be described with reference to FIG. FIG. 5 shows the vicinity of the contact surface between the outer ring member 2 and the mounting member 7, and the cross section is not hatched. In this embodiment, the outer ring member 2 is fitted into the mounting surface 7A of the mounting member 7 and is suitable for a rolling bearing used in a form in which the shaft member 8 is fixed and the mounting member 7 rotates as in the second embodiment. ing. In the second embodiment, the non-wear recess 22 is provided on the outer surface 2B of the outer ring member 2. However, in the fourth embodiment, the surface of the mounting member 7 that faces the outer surface 2B of the outer ring member 2 (hereinafter referred to as a facing surface). .) A non-wear recess 72 is formed in 71. The outer ring portion 2 is made of the porous material as described above. The structure in which the non-wear recess 72 is formed on the opposing surface 71 of the mounting member 7 without forming the non-wear recess 22 on the outer surface 2B of the outer ring member 2 is different from the second embodiment. Therefore, this difference will be described.

  The non-wear recess 72 formed on the facing surface 71 of the attachment member 7 may have the same shape and arrangement as the non-wear recess 22 formed on the outer surface 2B of the outer ring member 2 in the second embodiment. According to this structure, even if the fine hole H communicating with the outer surface 2B of the outer ring member 2 that contacts the facing surface 71 excluding the non-wear recess 72 of the mounting member is blocked by fretting and does not exude lubricating oil, The non-wear recess 72 of the mounting member 7 does not contact the outer surface 2B of the outer ring member 2, and the surface area of the outer surface 2B of the outer ring member 2 that does not contact does not wear. The fine holes H communicating with the surface area of the outer side surface 2B of the outer ring member 2 continue to exude lubricating oil. The lubricating oil that has oozed out spreads to the outer surface 2B of the outer ring member 2 by the rotation of the mounting member 7 and the relative minute movement that occurs at that time, and the same lubricating performance as in the second embodiment is maintained. Lifetime can be greatly improved.

  In the embodiment described above, the rolling element is described as a ball. However, the rolling element may be a general roller, a needle roller, a tapered roller, or the like. In this case, the rolling groove of the roller is generally often ground and finished, but may be a polished finish. At this time, the inner side surface of the inner ring member excluding the rolling groove or the outer side surface of the outer ring member excluding the rolling groove is hardly subjected to grinding or polishing, and may remain in a sintered state. The non-wear recess may be any shape such as a V shape or an arc shape. Although the sintered metal and the metal injection mold material are mentioned as the porous material, a porous material such as a ceramic material may be used. Of course, the rolling groove may be a recess that can omit the cage for holding the rolling element.

  In the first and third embodiments, the attachment member 7 is a rolling bearing housing, and the outer ring member and the housing member are fixed by press-fitting, and the housing is attached to a device (not shown) by simple attachment means such as screwing. When fixed, the outer ring member 2 need not be made of a porous material. However, in the case where the mounting member 7 is a fixing member for a device (not shown) and the outer ring member 2 is fitted into the fixing member so that the bearing can be easily attached and detached, the outer ring member 2 is the above-described embodiment. 2 or an outer ring member made of a porous material as described in the fourth embodiment.

It is drawing for demonstrating the rolling bearing which concerns on Embodiment 1 of invention. It is drawing for demonstrating the inner ring member of this rolling bearing. 6 is a view for explaining an outer ring member of a rolling bearing according to a second embodiment. It is drawing for demonstrating the rolling bearing which concerns on Embodiment 3. FIG. It is drawing for demonstrating the rolling bearing which concerns on Embodiment 4. FIG.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 ... Inner ring member 1A ... Inner side surface of inner ring member 1 1B ... Outer side surface of inner ring member 1 2 ... Outer ring member 2A ... Inner side surface of outer ring member 2 2B ... Outer ring member 2 Outer side surface 3 ... rolling element 4 ... cage 5 ... shield member 6 ... lubricant 7 ... mounting member 7A ... mounting surface of mounting member 7 8 ... shaft member 11. ..Rolling groove of the inner ring member 12... Non-wearing recess of the inner ring member 21... Rolling groove of the outer ring member 2 22... Non-wearing recess of the outer ring member 2 71. 7. Opposing surface 72 ... Non-wearing recess of mounting member 7 81 ... Opposing surface of shaft member 8 82 ... Non-wearing recess of shaft member 8 H ... Fine hole

Claims (6)

An inner ring member having a rolling groove on the outer side surface, an outer ring member having a rolling groove on the inner side surface, and a rolling element that rolls on the rolling groove, and is lubricated between the inner ring member and the outer ring member. In rolling bearings filled with agent,
The inner ring member has a fine hole communicating from the outer surface to the inner surface,
2. A rolling bearing according to claim 1, wherein a non-wear recess is formed on the inner side surface of the inner ring member so as not to contact a shaft member that is clearance-fitted to the inner ring member. An inner ring member having a rolling groove on the outer side surface, an outer ring member having a rolling groove on the inner side surface, and a rolling element that rolls on the rolling groove, and is lubricated between the inner ring member and the outer ring member. In rolling bearings filled with agent,
The outer ring member has a fine hole that communicates from the inner side surface to the outer side surface, and a non-wear recess is formed on the outer side surface of the outer ring member so as not to contact a mounting member that is clearance-fitted to the outer ring member. A rolling bearing characterized by An inner ring member having a rolling groove on the outer side surface, an outer ring member having a rolling groove on the inner side surface, a rolling element that rolls these rolling grooves, and a shaft member that is fitted in the inner side surface of the inner ring member In a rolling bearing formed by sealing a lubricant between the inner ring member and the outer ring member,
The inner ring member has a fine hole communicating from the outer side surface to the inner side surface,
The rolling bearing according to claim 1, wherein a non-wear recess is formed on a surface of the shaft member facing the inner ring member so as not to contact the inner side surface of the inner ring member. An inner ring member having a rolling groove on the outer side surface, an outer ring member having a rolling groove on the inner side surface, a rolling element that rolls on the rolling groove, and an attachment member that fits into the outer surface of the outer ring member. In a rolling bearing comprising a lubricant sealed between the inner ring member and the outer ring member,
The outer ring member has a fine hole communicating from the inner side surface to the outer side surface,
The rolling bearing according to claim 1, wherein a non-wear recess is formed on a surface of the mounting member that faces the outer ring member so as not to contact the outer surface of the outer ring member. In any one of Claim 1 thru | or 4,
The surface forming the rolling groove is smoothed by polishing or grinding,
The outer surface other than the rolling groove in the inner ring member, or at least a part of the inner surface other than the rolling groove in the outer ring member is not polished or ground, and the fine hole is not polished or ground. A rolling bearing characterized by being not blocked. In any one of Claims 1 thru | or 5,
A surface area in which the non-wear recess is formed and a surface area in which the non-wear recess is not formed in a facing surface between the inner ring member and the shaft member or a facing surface between the outer ring member and the mounting member. A rolling bearing characterized in that the ratio is in the range of 0.2 to 1.0.

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