JP2005054946A - Bearing device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a bearing device capable of enhancing mechanical durability of a vibration damping member provided on a bearing structure. <P>SOLUTION: In the bearing device comprising a bearing 10, a bearing supporting body 20 and a rotating body 22 with a vibration damping member S disposed between the bearing supporting body or the rotating body and the bearing, a groove forming a gap is formed in the surface of the vibration damping member or a surface facing the vibration damping member. When foreign matters enters between the vibration damping member and the member facing the vibration damping member, the foreign matters are captured in the cap and removed to avoid damages of the surface of the vibration damping member by the foreign matters, and pitching breakage of the vibration damping member. Complementary uneven grooves are formed in the vibration damping member and the member facing the vibration damping member so as to prevent relative slide between the vibration damping member and the member facing the vibration damping member, and occurrence of fretting wear or spalling breakage is suppressed. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

  The present invention relates to a bearing or a bearing device, and more particularly to the above-described device provided with a damping member that reduces vibration or noise. In the present specification, the “bearing device” is a device formed by combining a rotating body, a bearing that supports the rotating body, and a means or part that supports the bearing, that is, a “bearing support body”. Means any machine equipped with such a device structure, where the “bearing support” is composed of, for example, a housing removable from the machine body, or the machine body or frame. Including those that are integrally formed. Similarly, a “bearing support device” is a device that supports or holds a bearing, and should be understood to include one that is integrated into the body or frame of any machine.

  In various machines having a rotating body, a bearing that rotatably supports the rotating body, and a bearing support body configured on a machine body that holds the bearing or a case (bearing support device) provided in the machine. In some cases, a vibration damping member made of a material that hardly transmits vibration may be provided (the vibration damping member may be provided between the bearing and the rotating body). By providing such a damping member, mechanical vibration or noise of the rotating body, or mechanical vibration generated in a contact portion (or surface) between the bearing and the rotating body or a rolling element provided in the rolling bearing is provided. Propagation to the entire machine is avoided, and vibration or noise of the entire machine is suppressed. As such a damping member, generally, a polymer material having elasticity such as rubber or resin is widely used (for example, see Patent Documents 1 to 5 below). Further, in a bearing of a slightly large machine such as a transmission of a car or a transaxle, the weight of the rotating body to be supported by the bearing is large, and a high load acts on the bearing, thereby controlling the rubber or resin. The vibration member cannot withstand a high load applied to the bearing and is crushed. Thus, it has been proposed to use a metal (stainless steel) damping member (see Patent Document 6 below). In particular, the inventors of the present invention disclosed in Japanese Patent Application No. 2003-44508 and Japanese Patent Application No. 2003-89656 that the damping member has a high elastic modulus (that is, a small displacement even when subjected to a high load) and a vibration damping effect. A bearing structure is proposed which is made of a metal material having a large thickness (high vibration damping metal-see Patent Document 7 below) and can obtain a good vibration damping effect in consideration of the temperature or strain characteristics of the high vibration damping metal. In addition, Non-Patent Document 1 proposes the shape of a damping member that reduces vibration transmission of the rotating shaft by the applicant of the present application. However, at present, in the actual market, there are many cases where the vibration damping member is not provided.

  One problem with the high vibration damping metal (damping material) used as a damping material for the bearing device as described above is that the mechanical strength of the metal material is low. Various metals are known as metals having a good vibration damping effect. In general, however, the mechanical strength tends to decrease as the vibration damping capacity increases. As shown in FIG. 6, an alloy material that is effective as a damping material (for example, an Mn—Cu alloy, an Mg—Zr alloy, etc.) may have a lower tensile strength as the material has a larger damping coefficient. Has been found. Moreover, those strengths are lower than the aluminum alloy, cast iron, or bearing steel normally used for a case (refer nonpatent literature 2 below). Therefore, in the conventional bearing structure, even if a damping member made of a damping material selected as having a good vibration damping effect is incorporated, the damping member is susceptible to mechanical damage and mechanical Durability cannot be ensured (if a material with a high vibration damping effect is selected, the durability will be reduced accordingly).

  The mechanical damage (some of which) is a problem in the damping member is specifically related to the fit when the damping member is interposed between the case or the rotating body and the bearing, In particular, a relative (small) slip occurs between the damping member and the counterpart member as in the case where the fitting between the damping member and the counterpart member is a so-called “clearance fit”. Due to that. For example, in a bearing structure in which a high load acts on a bearing such as an automobile transmission as described above, when a damping member is interposed between the case and the bearing, the damping member In this case, with the rotation of the rotating body, the bearing between the damping member and the bearing In the meantime, relatively (slight) slip occurs, and at the same time, the damping member receives a high load surface pressure. Then, due to the high load surface pressure acting on the damping member and the relative slip between the bearings (and because the damping member has lower mechanical strength than the material of the bearing), the damping member Are susceptible to mechanical damage such as pitting or spalling failure, or fretting wear, as described below.

Therefore, in the conventional bearing structure or the structure of the damping member, if a material having a large vibration damping capability is selected as the material of the damping member, the mechanical durability of the damping member cannot be ensured, and the bearing device, particularly a large-sized It was difficult to implement effective anti-vibration / sound-proofing measures using practical damping members in machines.
Japanese Utility Model Publication No. 55-109134 Japanese Utility Model Publication No. 64-720 Japanese Patent Laid-Open No. 7-91443 JP-A-8-201715 Japanese Patent Laid-Open No. 2000-192979 Japanese Utility Model Publication No. 4-90718 Japanese Patent No. 2849698 Japan Society for Invention and Innovation Technical Bulletin No. 2002-2648 Issued on June 3, 2002 Magazine "Metal" Vol. 71 No.2 Page 47 2001 Agne Technology Center Co., Ltd.

  In the present specification, mechanical damage caused by the fitting between the vibration damping member and the bearing (or the bearing support device or the rotating body) in the bearing device as described above and the relative slip associated therewith is avoided or reduced. An invention is disclosed in which the mechanical durability of the damping member is improved, thereby expanding the range of selection of the damping material used as the damping member, and a material having a higher vibration damping capability can be adopted. The

  As described above, in the vibration damping member of the bearing device, mechanical damage called “pitching failure”, “spoling failure”, and “fretting wear” may occur.

  “Pitching fracture” is fatigue fracture that occurs when a crack is generated on the surface of a sliding member due to foreign matter (high hardness) entering between the sliding members, and the crack expands. That is, when a foreign object enters between members that cause relative slip, the foreign object moves while rolling with the relative slip. During operation of the bearing device, a considerable load is applied between the members in the device, so that the foreign object is pressed against the surface of the member by the load and damages the surface, and the scratch is the starting point. As a result, the cracks are enlarged due to the load between the members. Since a particularly high load is applied to a bearing such as a transmission of an automobile, a crack is likely to occur due to the entry of foreign matter, and the crack is likely to expand.

  “Spalling failure” means that a high stress is applied to the member, so that the shear stress inside the member exceeds the allowable limit stress of the internal defect or weak strength part (for example, heat treatment boundary) in the member. A part that exceeds the stress limit is a kind of fatigue fracture in which a crack is generated from the internal origin and reaches the surface. When a relative slip occurs between members subjected to a high load, the internal shear stress is further increased by the slip, and therefore, spalling failure is likely to occur.

  “Fretting wear” means that a minute slip is generated with a minute vibration transmitted from the outside between members that cause relative slip, and the surface is worn or oxidized by this. It is a phenomenon. The higher the load between the members that slide relative to each other, the stronger the force with which the surfaces of the members rub against each other.

  The series of mechanical damages described above is not a problem for the case and the bearing because the materials are sufficiently hard and have mechanical strength. However, as described above, the material of the damping member has a lower mechanical strength and is softer than the material of the case or the rotating body or the bearing steel, and thus is easily damaged. Thus, in order to ensure the mechanical durability of the damping member (see FIG. 6) whose mechanical strength is low in order to obtain a good vibration damping effect, the cause of the occurrence of such a series of mechanical damages. It will be necessary to remove the damage and prevent damage. It is also desirable to avoid such mechanical damage and to avoid the need for complicated mechanisms as cheap as possible.

  Thus, one problem to be solved by the present invention is a bearing device incorporating a vibration damping member that reduces vibration and noise, and a novel device that improves the mechanical durability of the vibration damping member for the bearing. It is to provide a bearing device having a simple structure.

  Another object of the present invention is a bearing device that supports a rotating body of a large machine such as an automobile, and includes the damping member that effectively reduces vibration and noise generated in the rotating body or the bearing. Is to provide such a bearing device.

  Still another object of the present invention is to provide a bearing device having a novel structure that eliminates the cause of mechanical damage of the vibration damping member and avoids or reduces such damage. That is.

  Still another object of the present invention is an apparatus as described above, which avoids or reduces mechanical damage caused by fitting between a damping member and a member fitted thereto and relative slippage between them. To provide a bearing device having a novel structure.

  A further object of the present invention is an apparatus as described above, in which mechanical damage is caused by relative slippage caused by fitting the damping member to another member by “clearance fitting”. It is an object of the present invention to provide a bearing device having a novel structure that avoids or reduces the above.

  A further object of the present invention is a device as described above, which has a novel structure capable of preventing the occurrence of “pitching failure”, “spalling failure” or “fretting wear” in a damping member. It is providing the bearing apparatus which has.

  Still another object of the present invention is to employ a device as described above, which has a wide range of choices of materials that can be used as the damping member, and therefore employs a material having a higher vibration damping capability. By making it possible to provide a bearing device having a novel structure capable of obtaining a good vibration damping effect.

  Still another object of the present invention is an apparatus as described above, which is a novel structure capable of avoiding the above-described mechanical damage of the damping member without requiring an inexpensive or complicated structure. It is providing the bearing apparatus of this.

  According to the present invention, the above-described problem includes a bearing, a bearing support that supports the bearing, and a rotating body that is attached to the bearing, and is provided between at least one of the bearing support and the rotating body and the bearing. The vibration damping member is provided with a groove on the surface of the vibration damping member and at least one of the surface of the bearing, the bearing support or the rotating body facing the vibration damping member. The groove forms a gap, whereby foreign matter that has entered between the surface of the damping member and the surface of the bearing, bearing support or rotating body facing the damping member is captured in the gap. This is achieved by the bearing device.

  As described above, one cause of the mechanical damage that occurs in the vibration damping member is that a foreign material having a hardness higher than that member enters between the members that can slide with each other. It was to hurt. Therefore, in the configuration of the bearing device described above, when the foreign matter causing the pitching breakage enters between the surface of the vibration damping member and the surface of the member facing it, the foreign matter continues to move between the surfaces. In order to prevent this, a groove forming a gap is provided on the vibration damping member or the member facing it. Thus, even if a foreign object enters between the surfaces, it can be trapped by falling into the gap while moving on the surface, and thereafter the surface of the member can be prevented from moving and being damaged. become.

  The “groove”, which is a feature of the present invention, can be easily provided on the surface of the damping member in the production of the bearing device, for example, when the damping member is incorporated into an existing or general-purpose bearing device. Although it seems to be advantageous (the damping member is generally softer than the material for the case or bearing steel etc.), it should be understood that it may be provided on the side of the member facing the damping member It is. As described in Japanese Patent Application No. 2003-44508 and Japanese Patent Application No. 2003-89656 proposed by the present inventor, the vibration damping member has a vibration or noise generation site to be suppressed and its characteristics. It is arbitrarily provided between the bearing and the bearing support or between the bearing and the rotating body. Therefore, the groove may be arbitrarily provided on a member such as a bearing, a bearing support body, or a rotating body that faces the surface of the vibration damping member that may cause the pitching failure depending on a portion where the vibration damping member is provided. It should be understood that all such configurations are within the scope of the present invention.

  By the way, as already described, one of the factors that cause the pitching failure is the relative slip between the facing members. For example, relative slip occurs between the members that have been “clearance fitted” in the bearing device as the rotating body rotates. According to the present invention, the surface of the vibration damping member that is fitted with the “clearance fit” or the surface of the member facing the surface is provided with the groove of the present invention, so that the surfaces sliding with each other are provided. Foreign matter is removed from the gap, and pitching destruction can be prevented.

  Further, when a load that presses each other is applied between the sliding members, the foreign matter is strongly pressed against the surface of the member, and the surface is likely to be damaged, so that the pitching breakage easily occurs. In particular, depending on the type of the bearing device, for example, in a tapered roller bearing used for a bearing portion of an automobile transmission, a preload is applied to the bearing outer ring, but the vibration damping member receives a preload applied to the bearing. When arranged, the vibration damping member and the member facing it are pressed against each other, which can cause pitching failure. Similarly, during operation of the bearing device, a thrust load may act on the various members in the bearing device generally in the direction in which the rotation axis of the rotating body faces, that is, in the thrust direction. Is disposed at a position that receives such a thrust load, the surface of the damping member is damaged by foreign matter that has entered between the members. However, according to the present invention, when the damping member is disposed at a position to receive the preload or the thrust load, the present invention is applied to the surface of the damping member that receives the preload or the thrust load or the surface of the member facing the surface. By providing the groove, it is possible to trap the foreign matter between the sliding surfaces and greatly reduce the possibility of the occurrence of pitching failure.

  Usually, the preload or thrust load acts substantially parallel to the rotation axis of the rotating body and the bearing. Further, in the bearing device, generally, the radial direction of the bearing is often required to have higher track accuracy than the thrust direction, that is, the direction along the rotation axis of the bearing. Therefore, it is preferable that the outer peripheral surface and the inner peripheral surface of the bearing are not processed as much as possible. That is, the groove of the present invention is preferably provided on the thrust surface of a vibration damping member having a surface (thrust surface) extending in a direction substantially perpendicular to the rotation axis or in the radial (radiating) direction of the bearing.

  According to the second aspect of the present invention, the above problem includes a bearing, a bearing support that supports the bearing, and a rotating body that is mounted on the bearing, and at least one of the bearing support and the rotating body. Device comprising a vibration damping member between the bearing and the bearing, wherein the surfaces of the vibration damping member and the surface of the bearing, bearing support or rotating body facing each other are fitted together The concave and convex grooves fitted to each other prevent the displacement in the rotational direction of the bearing relative to the damping member and the bearing, bearing support or rotating body facing the damping member. This is achieved by the bearing device.

  As described above, if relative slip occurs between the vibration damping member and the bearing, bearing support or rotating body facing the vibration damping member, not only pitching failure but also fretting wear may occur. Fretting wear gradually progresses as long as the surfaces of the sliding members rub against each other due to relative slip. Therefore, in the second aspect of the present invention described above, complementary vibration grooves (that is, a relationship between a key and a key hole) are provided on the surface facing the vibration damping member and the vibration damping member, It is configured to prevent displacement in the rotational direction of the bearing relative to the bearing, bearing support or rotating body facing the vibration damping member, that is, relative slippage, and suppress occurrence of surface wear.

  Since the purpose of the concave and convex grooves is to prevent relative slip between members, the gap is formed as long as the objective can be achieved with the concave and convex grooves fitted. It may be. According to such a gap, it becomes possible to absorb the difference in thermal expansion of the members during operation of the bearing device or to trap foreign matter that has entered between the members.

  In the second aspect of the present invention described above, when at least a part of the vibration damping member has a portion that receives a load in the thrust direction, the concave and convex grooves face the surface of the portion of the vibration damping member that receives the thrust load and the surface thereof. It is preferable to be provided on the surface of the bearing, bearing support or rotating body.

  As already described, it is preferable that the outer peripheral surface and the inner peripheral surface of the bearing are not processed as much as possible. Therefore, it is preferable that the groove for the purpose of preventing the relative slip is provided on the surface that receives the thrust load, that is, the surface that is substantially perpendicular to the rotation axis of the bearing, or the surface that intersects the outer peripheral surface or the inner peripheral surface. .

  The shape of the concavo-convex groove may be any that can prevent relative slip. Conversely, a groove having only a surface that engages only in the direction along the rotation direction of the bearing, for example, a concentric annular groove around the rotation axis of the bearing cannot prevent relative slip. That should be understood.

  Further, according to the third aspect of the present invention, in the case where the complementary concave-convex grooves as described above are formed on the surface that receives the thrust load, the extending direction of each surface of the groove is determined by the thrust load. If it is inclined at an arbitrary angle so as to be inclined with respect to the acting direction, that is, not perpendicular to the acting direction of the thrust load, the occurrence of the above-mentioned “spoling failure” is caused. It can be avoided or reduced. As already mentioned, spalling failure is caused by the expansion of cracks caused by the internal stress of a member exceeding the allowable limit stress of the member. According to the third aspect of the present invention described above, By inclining the direction of the surface with respect to the thrust load, the internal stress generated by the thrust load applied to the surface of the member is dispersed, thereby avoiding the generation of a locally high stress and the stress in the member. However, it is possible to reduce the possibility of exceeding the allowable limit that may cause cracks, and thus to suppress the occurrence of spalling failure.

  If the relative slip between the members is prevented, the shear stress applied to the surface due to such slip is reduced, so that the uneven groove for avoiding spalling failure is preferably in the second aspect of the present invention. It is preferable that the groove is formed in a direction that can prevent relative slippage between the members in the same manner as the concave and convex grooves. However, the purpose of avoiding a local increase in internal stress in the member is to a certain extent even if the groove is formed in a direction allowing relative sliding (in a concentric ring centered on the rotation axis of the bearing). It should be understood that this is achieved, and bearing devices including such grooves are included within the scope of the present invention. Furthermore, in order to avoid an increase in local internal stress over the entire surface of the portion subjected to the thrust load, a plurality of concave and convex grooves are provided on the surface of the vibration damping member that receives the thrust load and the surface of the member facing it. Preferably, a plurality of concave and convex grooves extending in the radial direction of the bearing are formed over the entire circumference in the circumferential direction of the bearing.

  The configuration for avoiding or reducing the mechanical damage of the damping member in the present invention described above may be provided individually for each of the damping member, the bearing, the bearing support device, or the rotating body. It will be understood that the damping member, bearing, bearing support device or rotating body having the features of the invention can be used in combination with a general purpose bearing, bearing support device or rotating body. For example, a vibration damping member configured to be interposed between a bearing and a bearing support that supports the bearing or a rotating body that is mounted on the bearing, the bearing, the bearing support, or the rotating body A vibration damping member characterized in that a groove is provided on the facing surface to form a gap is used in an existing bearing device between a bearing and a bearing support or a rotating body. And can be advantageously used as a damping member having mechanical durability.

  As already mentioned, in the prior art, a high-weight machine or device cannot use a polymer material such as a rubber elastic body as a vibration damping member. In practice, the vibration damping member itself is almost always used. Although not used, the inventors of the present invention disclosed in Japanese Patent Application No. 2003-44508 and Japanese Patent Application No. 2003-89656 that a damping material capable of withstanding a large weight, such as a high elastic modulus and high vibration damping metal. Has been proposed to be used as a damping member for a bearing device. In the present invention, a means for ensuring the mechanical durability of a vibration damping member made of a metal having a high elastic modulus and high vibration damping is provided, so that conventionally, the vibration damping treatment by the vibration damping member cannot be performed. In addition, in a medium- or large-sized machine or device, it is possible to practically use a damping member made of a high elastic modulus and high vibration damping metal as described above.

  One of the advantages of the present invention is that it should be noted that the effect of the present invention, that is, the improvement of the durability of the vibration damping member, improves the surface shape of the vibration damping member or the member facing it. It is obtained by adding, and is independent of the type of damping material. According to this advantage of the present invention, the range of types of materials that can be employed as the damping member is greatly expanded, and the material plotted on the upper left of the damping material in FIG. 6 can be selected as appropriate. Therefore (note that the vertical and horizontal axes in FIG. 6 are logarithmic), a material having a much better vibration damping effect can be practically used.

  As a further advantage of the present invention, measures to prevent mechanical damage are achieved by forming a groove in the damping member or the member facing it without requiring additional members in the device. Thus, it should be noted that it is not structurally complex and does not significantly increase the manufacturing cost of the device. As will be understood from the detailed description in the following embodiments, for example, by forming a groove which is a feature of the present invention in the damping member, there is no or almost no design change in the existing bearing device. It is very advantageous that the effects of the present invention can be obtained.

  The characteristic configuration of the present invention described above may be applied not only to a transmission such as an automobile and a power transmission device but also to various heavy machines or bearing devices. Also, even in the conventional bearing device using a damping member made of rubber or the like, the damping material is usually softer and more susceptible to mechanical damage than the bearing or case material, If the configuration of the present invention is applied, the durability of the damping member can be improved and the life of the damping member can be extended.

  Other objects and advantages of the present invention will become apparent from the following description of preferred embodiments of the present invention.

  The present invention will now be described in detail with reference to a few preferred embodiments with reference to the accompanying drawings. In the figure, the same reference numerals indicate the same parts.

  In the following, the present invention will be described with reference to a rolling bearing typically found in a power transmission device such as an automobile, and more specifically, a form applied to a tapered roller bearing. It will be understood that the invention is equally applicable to any other rolling bearing or bearing structure including a plain bearing and any machine or apparatus having a bearing structure without departing from the scope. .

  FIG. 1 is a schematic cross-sectional view of a structure around a bearing in a transaxle of an automobile or the like to which the present invention is applied. In the drawing, a bearing indicated by reference numeral 10 is a tapered roller bearing, and a plurality of rollers or rolling elements 16 are provided between an annular bearing outer ring 12 and a bearing inner ring 14 centered on a line CL. Is held and can roll (only two rolling elements are shown in the figure for the sake of simplicity). The bearing outer ring 12 is fixedly held by a bearing support or case 20 formed on the frame of the machine main body (transaxle in the illustrated example). On the other hand, the bearing inner ring 14 is fixedly held on the rotating body 22 of the machine. The rotating body 22 is formed with a gear 24 at a portion different from the portion where the bearing is provided, and is operatively engaged with a gear of another rotating body (not shown). Thus, as is well known, when the rotating body 22 rotates around the rotation axis CL, the bearing inner ring 14 rotates together with the rotating body 22, whereby the rolling element 16 moves between the bearing inner ring 14 and the bearing outer ring 12. Roll. Each element of the bearing may be formed of any bearing steel known to those skilled in the art, for example, high carbon chrome steel (any material selected to meet the requirements of the type of machine or the bearing employed). Good.)

  In a machine provided with a bearing structure as shown in the figure, vibration or noise is caused by impact vibration caused by meshing between a gear 24 of a rotating body and a gear (not shown) of another rotating body or rotation of a rolling element of a bearing. Due to vibration. In order to prevent those vibrations from being transmitted to the bearing support via the bearing, in the embodiment of the present invention in FIG. 1, a damping member S is provided between the bearing support 20 and the bearing outer ring 12. The damping member S absorbs vibration generated in the rotating body or the bearing, and thus vibration transmitted to the bearing support 20 is reduced. The damping member S may be formed of a high elastic modulus and high vibration damping metal as described in Japanese Patent Application Nos. 2003-44508 and 2003-89656. For example, K1X1 (Mg—Zr alloy) that is a dislocation type high vibration damping metal, M2052 (Mn—Cu alloy) that is a twin type high vibration damping metal, or the like is employed. It is understood that the damping member S is preferably provided along the outer or inner peripheral surface of the bearing and thus has an annular sleeve shape in that case, although not fully illustrated. It should be.

  In the bearing structure as shown in FIG. 1, when the rotating body 22 is fitted to the bearing inner ring 14, the fitting is typically an interference fit. On the other hand, the bearing outer ring 12 is fitted to the bearing support so as to have a clearance fit. Therefore, as shown in the example of FIG. 1, when the damping member S is interposed between the bearing outer ring 12 and the bearing support 20, the fit between the damping member S and the bearing support 20 is tight. A clearance fit is provided between the damping member S and the bearing outer ring 12. Of course, the fitting of these members is suitably designed to provide an interference fit between the damping member S and the bearing outer ring 12 and a clearance fit between the damping member S and the bearing support 20. It should be understood by those skilled in the art that it may be. Further, the damping member S may be mounted between the bearing inner ring 14 and the rotating body 22, and the fit between the damping member S and the bearing inner ring 14 or the rotating body 22 is arbitrarily fit. It will also be appreciated that the dimensions of the member may be designed to provide a clearance fit.

  As described in the section of the disclosure of the invention, the material of the vibration damping member S generally has a mechanical strength lower than that of the bearing support or the bearing material. It is easily damaged and cannot ensure mechanical durability. In particular, in a configuration in which relative slippage may occur, such as when the vibration damping member S and a member facing it are loosely fitted, pitching failure, spalling failure, or fretting wear occurs as described above. Cheap. In the example of FIG. 1, since the clearance between the damping member S and the bearing outer ring 12 is a clearance fit, there is a possibility that the mechanical damage as described above may occur starting from the surface thereof.

  Therefore, in the bearing device illustrated in FIG. 1, first, a pitting breakage, that is, foreign matter having a high hardness, particularly harder than the damping member S, is present between the damping member S and the bearing outer ring 12 facing the damping member S. In order to avoid destruction due to entering, a plurality of grooves 30 are provided on the surface of the damping member S, and the grooves 30 are configured to form voids on the surface. 2A shows a schematic diagram of the vibration damping member S on a plane perpendicular to the rotation axis of the bearing as seen in the direction of the arrow in FIG. 2 along the line II-II in FIG. FIG. 2B is a cross-sectional view of the vibration damping member S and the bearing outer ring 12 as viewed in the direction of the arrow in the drawing along line BB in FIG. As understood from these drawings, for example, a plurality of grooves 30 may be provided so as to extend in the radial direction of the damping member around the rotation axis CL. By forming the groove 30, foreign matter from the outside enters between the damping member S and the member facing the damping member S (the bearing outer ring 12 in the example of FIG. 1) during assembly or operation of the bearing device. Even if it enters, while the vibration damping member S and the bearing outer ring 12 slide relative to each other, foreign matter falls into the groove 30 and is trapped, and thus from between the surfaces of the vibration damping member S and the bearing outer ring 12 that rub against each other. Removed to avoid pitching failure. Further, the inner end 30a of the groove 30 may be opened, and in this case, the foreign matter that has fallen into the gap may be removed from the inner end 30a.

  The shape of the groove 30 may be configured to extend radially around the rotation axis CL as shown in FIG. 2A, but the damping member S as shown in FIG. A plurality of indented grooves 32 may be appropriately dispersed on the surface. In this case, considering that the relative slip between the damping member S and the bearing outer ring 12 is a rotational displacement around the rotation axis CL, the entire surface of the damping member S is covered while the rotational displacement occurs. The depressions 32 are preferably formed so as to be shifted from each other in the radial direction of the damping member S so as to be able to do so.

  In the example of FIGS. 1 and 2, it is noted that the groove 30 or 32 is formed not in the portion S1 facing the cylindrical surface 12a around the bearing but in the portion S2 that is substantially perpendicular to the rotation axis CL. Should. Normally, the cylindrical surface 12a of the bearing is required to have a high degree of orbit accuracy in order to ensure rotational accuracy. Therefore, it is desirable not to form an additional structure such as a groove as much as possible in the portion S1 facing the cylindrical surface 12a around the bearing. On the other hand, the portion S2 that is substantially perpendicular to the rotation axis CL receives a load (thrust load) in the thrust direction generated between the bearing support and the rotating body. When acting between the member S2 and the member (bearing outer ring) facing the member, the foreign matter is pressed against the surface of the vibration damping member (and the member facing the member) and is damaged. Further, the tapered roller bearing as shown in the figure operates by applying a preload to the bearing by pressing the rotating body 22 toward the bearing support body 20 along the rotation axis CL. In such a case, the preload also acts on the surface S2 of the vibration damping member S, and as a result, the surface S2 of the vibration damping member S sandwiching the foreign matter is damaged as in the case where a thrust load is applied. Become. Therefore, as shown in the figure, the groove 30 or 32 is preferably formed on the surface S2 at a site substantially perpendicular to the rotation axis CL so that the foreign matter that has entered the surface receiving the thrust load or preload is removed. The surface S2 of the vibration receiving member S that receives the thrust load does not need to be substantially perpendicular to the rotation axis CL as shown in the figure, and may be a surface of a portion having an arbitrary shape depending on the shape of the bearing outer ring. That should be understood.

  If the orbit accuracy on the cylindrical surface 12a of the bearing is appropriately ensured, a groove 30 may be provided on the cylindrical surface 12a (see FIG. 3A), in which case the surface S1 of the damping member and Foreign matter that has entered between the cylindrical surface 12a of the bearing is removed.

  It should be understood that similar grooves may be provided on the bearing outer ring 12, such as grooves 30 ', as shown in FIG. Further, when the damping member S is fit into the bearing and the clearance between the damping member S and the bearing support 20 is a clearance fit, it faces the bearing support 20 of the damping member S. A groove 30 ″ may be provided on the side (FIG. 3C). Further, when the damping member S is provided only on a surface substantially perpendicular to the rotation axis CL of the bearing, the same groove 30 is provided on the damping member. It may be configured so as to be provided on S or on a member facing it (FIG. 3D) A similar groove is also provided when the damping member S is provided between the bearing inner ring 14 and the rotating body 22. May be formed.

  The vibration damping member S provided with the groove 30 as shown in FIG. 1 or FIG. 3 (A) has a good vibration damping effect and is a general-purpose or existing vibration damping member with mechanical durability. It should be understood that such a vibration damping member itself is a form of the present invention.

  FIG. 4 shows a second embodiment of the present invention, in which (A) is a cross-sectional view along the rotation axis CL of the bearing device similar to FIG. 1, and (B) is shown in (A). It is a schematic diagram of the cross section seen from line BB in this, (C) is an expanded sectional view of the damping member S and the bearing outer ring 12 seen along line CC in (B). In this embodiment, complementary concave and convex grooves 40a (protrusions on the vibration damping member S side) and 40b (protrusions on the bearing outer ring 12 side) are provided on the surfaces of the vibration damping member S and the bearing outer ring 12, Relative slipping of these members is prevented, and not only pitching failure but also fretting wear occurring in the vibration damping member is avoided.

  Also in the structures shown in these drawings, the damping member S is provided between the bearing 10 and the bearing support 20, and a clearance fit is provided between the damping member S and the bearing outer ring 12. Therefore, if the concave and convex grooves 40a and 40b are not present, both members should be relatively slippery in the rotational direction as the rotating body 22 rotates. The relative slip is prevented by fitting the concave portion or the convex portion of the damping member S with the convex portion or the concave portion on the bearing outer ring 12 in relation to the key hole.

  The concave and convex grooves 40a and 40b may be formed on the cylindrical surface 12a of the bearing. However, the cylindrical surface 12a is preferably understood from FIG. Thus, it is formed on a surface substantially perpendicular to the rotation axis CL (similar to the example of FIG. 1).

  Further, as shown in FIG. 4B, the concave and convex grooves 40a and 40b are typically formed so as to extend in the radial direction from the rotation axis CL, but the vibration damping member S and the bearing outer ring 12 are also formed. Those skilled in the art will appreciate that can be formed in any pattern that can prevent relative displacement in the rotational direction. As shown in FIG. 4C, the concave and convex grooves may be rectangular or other shapes. What is important is that the surfaces of the grooves engaged with each other extend in a direction in which the relative rotational direction between the damping member S and the bearing outer ring 12 does not coincide (the tangential direction of the surface does not coincide with the displacement direction). It is formed to exist. Further, as will be described in detail with reference to FIG. 5 below, the shape of the concavo-convex groove may be arbitrarily determined in order to achieve an object other than preventing relative slippage. Further, in the state in which the concave and convex grooves are fitted to each other, a gap 40c may be provided, so that foreign matter that has entered between the surfaces can be trapped or a difference in thermal expansion between the members can be accommodated. Good.

  Thus, as shown in FIG. 4, by providing the complementary concave-convex grooves, relative slip between the vibration-damping member S and the bearing outer ring 12 which are fitted by clearance is avoided, and the pitching failure In addition, fretting wear can be suppressed. As in the example of FIG. 1, the concave and convex grooves in FIG. 4 are formed when the clearance between the damping member S and the bearing support 20 is a clearance fit or between the rotating member and the bearing. It should be understood that it may be appropriately provided between members that cause relative slip to each other in such a case (other than between the damping member S and the bearing outer ring 12). B) Bearing devices, bearings, bearing supports or rotating bodies provided with concave and convex grooves belong to the scope of the present invention.

  FIG. 5 shows a bearing device substantially similar to the embodiment of FIG. 4, but as can be seen from FIGS. 5 (B) and 5 (C), complementary irregularities formed on the surface receiving the thrust load. The surfaces of the grooves 44a and b are configured to extend at an angle with respect to the rotation axis CL. That is, as shown in FIG. 5C, the concavo-convex grooves to be fitted to each other have a sawtooth cross section having a top portion and a trough portion. As a result, spalling failure is avoided or reduced in addition to pitching failure and fretting wear, as will be described below.

  Referring to FIG. 5D, on the damping member extending in a direction substantially perpendicular to the rotation axis CL, the thrust load or the preload force F1 of the bearing acts in a direction parallel to the rotation axis CL. To do. In the case of the concavo-convex groove as shown in FIG. 4, the surface of the groove receives the force F1 as it is, and thus a strong stress can be locally generated inside the surface. In that case, when the locally strong stress reaches a relatively low part of the allowable stress, a crack is generated in the low part, and the crack is enlarged by the stress derived from the force F1. Can cause spalling destruction. However, in this embodiment, the surface of the groove is inclined with respect to the rotational axis CL so as to extend at a certain angle, so that the surface is inclined with respect to the force F1. , The force is distributed and high local stresses are avoided. Thus, the probability of occurrence of cracks inside the surface is reduced, and the risk of spalling failure can be reduced.

  As shown in FIG. 4C, the gap 44c may be formed also in the complementary concave-convex groove of this embodiment. Further, since it is desirable that the force is distributed over the entire surface of the damping member S that receives the thrust load, the concave and convex grooves are preferably formed on the entire surface S2 of the damping member S and the bearing outer ring 12 facing the entire surface. It is preferable to be provided on the surface.

  Furthermore, although not shown in the drawing, if only the purpose of distributing the thrust load (or preload) applied to the damping member S is achieved, the extending direction of the groove is determined by the damping member S and the bearing outer ring 12. It should be understood that they may be provided concentrically in a direction that allows relative sliding of them, for example, about the rotation axis CL. Further, it should be understood that the present invention can also be applied to the case where the damping member S is not provided on the cylindrical surface 12a of the bearing but only on the surface receiving the thrust load. It is obvious to those skilled in the art that the same configuration as that shown in FIG. 5 can be formed even when the damping member is mounted between the rotating body and the bearing inner ring. It should be understood that it belongs to the scope of the invention.

  Thus, according to the embodiment as shown in FIG. 5, by distributing the force applied to the damping member S, in addition to pitching failure and fretting wear, the possibility of occurrence of spalling failure is reduced. Thus, the mechanical durability of the damping member can be ensured.

  Although the above description has been made in connection with the embodiments of the present invention, it should be understood that many modifications and changes can be easily made by those skilled in the art. It will be understood that the invention is not limited to the embodiments illustrated in FIG. 1 and applies to various devices without departing from the inventive concept.

The schematic diagram of the bearing structure by which the damping member by this invention was interposed between the bearing support body and the bearing. (A) Sectional drawing of the bearing apparatus along the rotation axis CL of a bearing. (A) The schematic diagram of the damping member S seen from the line II-II of A. (B) The schematic diagram of the cross section of the groove part of the damping member S and the bearing outer ring | wheel 12 seen from line BB of A. FIG. (C) The same figure as (A) about another embodiment of the present invention. (A) The schematic diagram of the bearing structure similar to FIG. 1 of embodiment by this invention provided in the site | part in which the groove | channel of the damping member faces the cylindrical surface of a bearing. (B) A schematic view of a bearing structure similar to FIG. 1 of the embodiment according to the present invention in which a groove 30 ′ is provided on the bearing outer ring 12. (C) A schematic diagram of a bearing structure similar to that of FIG. 1 of the embodiment according to the present invention in which a groove 30 ″ is provided on the side facing the bearing support 20 of the damping member S. Only the upper half of the cross section of the bearing structure. The lower half is omitted because it is symmetrical with respect to the rotation axis CL. (A) The schematic diagram of the bearing structure similar to FIG. 1 of embodiment by this invention in which the complementary uneven groove | channel of the damping member S and the bearing outer ring | wheel 12 was formed. The uneven grooves are indicated by broken lines. Only the upper half of the cross section of the bearing structure is shown, and the lower half is omitted because it is symmetric with respect to the rotation axis CL. (B) The schematic diagram of the damping member S seen from the line BB of A. (C) The schematic diagram of the cross section of the groove part of the damping member S and the bearing outer ring | wheel 12 seen from B line CC. (A) A bearing structure similar to that of FIG. 1 of the embodiment according to the present invention, in which grooves are formed by complementary grooves between the damping member S and the bearing outer ring 12 and have a surface inclined with respect to the rotation axis CL. FIG. (B) The schematic diagram of the damping member S seen from the line BB of A. (C) The schematic diagram of the cross section of the groove part of the damping member S and the bearing outer ring | wheel 12 seen from B line CC. (D) The figure which shows that the force which acts on the surface of a groove | channel is disperse | distributed. The graph figure which shows the relationship between the vibration damping factor (damping coefficient) and mechanical strength (tensile strength) of the metal material used for various cases or bearings, and a high vibration damping metal material (cited from nonpatent literature 2).

Explanation of symbols

DESCRIPTION OF SYMBOLS 10 ... Bearing 12 ... Bearing outer ring 12a ... Bearing cylindrical surface 14 ... Bearing inner ring 16 ... Rolling element (roller)
20 ... Case (bearing support)
22 ... Rotating body 24 ... Gear 30 ... Groove 32 ... Dimple (groove)
40a, b ... Uneven groove 40c ... Air gap 44a, b ... Uneven groove 44c ... Air gap CL ... Rotational axis S ... Damping member S1 ... Surface of the damping member facing the cylindrical surface of the bearing S2 ... Damping member receiving thrust load Face of

Claims (37)

  A bearing includes a bearing, a bearing support that supports the bearing, and a rotating body mounted on the bearing, and a vibration damping member is provided between at least one of the bearing support and the rotating body and the bearing. A groove is provided on at least one of the surface of the damping member and the surface of the bearing, bearing support or rotating body facing the damping member, and the groove A gap is formed, whereby foreign matter that has entered between the surface of the damping member and the surface of the bearing, bearing support, or rotating body facing the damping member is captured in the gap. Bearing device.   The bearing device according to claim 1, wherein the damping member has a surface fitted in a clearance fit with respect to the bearing, the bearing support body, or the rotating body, and the groove serves as a clearance fit of the damping member. A bearing device, wherein the bearing device is provided on at least one of a surface of the surface and the surface of the bearing, the bearing support or the rotating body facing each other.   2. The bearing device according to claim 1, wherein preload is applied to the bearing, and the groove receives at least the surface of the vibration damping member that receives the preload and the surface of the bearing, the bearing support, or the rotating body facing the surface. A bearing device provided on one surface.   2. The bearing device according to claim 1, wherein the damping member has a thrust surface that receives a thrust load from the rotating body, and the groove is a surface of the thrust surface of the damping member and the bearing facing the thrust surface, the bearing support. A bearing device, wherein the bearing device is provided on at least one of the surfaces of the body and the rotating body.   The bearing device according to claim 1, wherein the bearing is a tapered roller bearing. A bearing support device configured to support a bearing, wherein a damping member is provided at a portion facing the bearing when the bearing is mounted,
A groove is provided on the surface facing the vibration damping member, and the groove forms a gap when the vibration damping member is mounted, whereby the surface of the vibration damping member and the surface facing the vibration damping member The bearing support device is characterized in that the foreign matter that has entered between is captured in the gap.   The bearing support device according to claim 6, wherein at least a part of the vibration damping member is disposed in a portion that receives a thrust load, and the groove is provided on a surface facing at least a part of the vibration damping member. A bearing support device characterized by being provided.   The bearing support device according to claim 6, wherein at least a part of the vibration damping member is disposed at a portion that receives a preload applied to the bearing, and the groove faces at least a part of the vibration damping member. A bearing support device provided on a surface of the bearing.   The bearing support device according to claim 6, wherein the fitting with the vibration damping member on the surface facing the vibration damping member is a clearance fit.   A rotating body mounted on a bearing, wherein the rotating body is configured to be provided with a damping member at a portion facing the bearing when mounted on the bearing. A groove is provided on the surface, and when the vibration damping member is mounted, the groove forms a gap, so that foreign matter that has entered between the surface of the vibration damping member and the surface facing the vibration damping member A rotating body characterized by being trapped in the gap.   The rotating body according to claim 10, wherein at least a part of the vibration damping member is interposed in a portion where a thrust load is applied to the bearing when being mounted on the bearing, and the groove is the vibration damping member. A rotating body provided on a surface facing at least a part of a member.   11. The rotating body according to claim 10, wherein the fitting with the damping member on the surface facing the damping member is a clearance fit.   A bearing having an outer peripheral surface and an inner peripheral surface, wherein a vibration damping member is provided on at least one of the outer peripheral surface and the inner peripheral surface, and a groove is provided on a surface facing the vibration damping member. When the vibration damping member is mounted, the groove forms a gap, whereby foreign matter that has entered between the surface of the vibration damping member and the surface facing the vibration damping member is captured in the gap. A bearing characterized by being made.   14. The bearing according to claim 13, wherein at least a part of the vibration damping member is disposed at a site to receive a thrust load when the rotating body is mounted on a bearing support device that supports the bearing. The groove is provided on a surface facing at least a part of the damping member.   14. The bearing according to claim 13, wherein the bearing is operated by applying a preload, and the preload acts on at least a part of the damping member when the damping member is mounted on the bearing. The groove is provided on a surface facing at least a part of the damping member.   14. The bearing according to claim 13, wherein the fitting with the damping member on the surface facing the damping member is a clearance fit.   A vibration-damping member configured to be interposed between a bearing and a bearing support that supports the bearing or a rotating body that is mounted on the bearing, wherein the bearing, the bearing support, or the rotating body A vibration damping member, characterized in that a groove is provided on the surface facing to form a gap.   18. The vibration damping member according to claim 17, further comprising a portion that receives a thrust load when interposed between the bearing and the bearing support or the rotating body, and the groove receives the thrust load. A vibration damping member provided on a surface of a part.   18. The vibration damping member according to claim 17, wherein when the groove is interposed between the bearing and the bearing support body or the rotating body, the bearing, the bearing support body, or the rotating body. A vibration damping member, characterized in that the fitting is provided on a surface that provides a clearance fit.   A bearing includes a bearing, a bearing support that supports the bearing, and a rotating body mounted on the bearing, and a vibration damping member is provided between at least one of the bearing support and the rotating body and the bearing. Complementary concavo-convex grooves that are fitted to each other are provided on the surface of the damping member and the surface of the bearing, bearing support, or rotating body facing the damping member. The fitted concave and convex grooves prevent the displacement in the rotational direction of the bearing relative to the vibration damping member and the bearing, bearing support or rotating body facing the vibration damping member. .   21. The bearing device according to claim 20, wherein the concave and convex grooves fitted to each other form a gap.   21. The bearing device according to claim 20, wherein at least a part of the vibration damping member has a portion that receives a load in a thrust direction, and the concave and convex grooves face a surface of a portion of the vibration damping member that receives the thrust load. A bearing device provided on a surface of the bearing, the bearing support or the rotating body.   A bearing includes a bearing, a bearing support that supports the bearing, and a rotating body attached to the bearing, and a vibration damping member is provided between at least one of the bearing support and the rotating body and the bearing. In this bearing device, at least a part of the damping member has a portion that receives a load in a thrust direction, and complementary concave and convex grooves that are fitted to each other are parts of the portion of the damping member that receives the thrust load. A plurality of surfaces are formed over the entire surface of the bearing, the bearing support or the rotating body facing the surface, and each surface of the concave and convex grooves extends in a direction inclined with respect to the acting direction of the thrust load. A bearing device characterized by that.   A bearing support device for supporting a bearing, wherein a vibration damping member is provided at a portion facing the bearing when the bearing is mounted, the surface of the vibration damping member and the vibration damping member. Complementary concavo-convex grooves that are fitted to each other are provided on the surface of the bearing support device facing the member, and the concavo-convex grooves are relative to the vibration damping member and the bearing support device facing the vibration suppression member. A bearing support device that prevents displacement of the bearing in the rotational direction.   25. The bearing support device according to claim 24, wherein the concave and convex grooves fitted to each other form a gap.   25. The bearing support device according to claim 24, wherein at least a part of the vibration damping member receives a load in a thrust direction when the bearing and a rotating body mounted on the bearing are mounted, and the unevenness A bearing support device, wherein a groove is provided on a surface of a portion of a vibration damping member that receives the thrust load and a surface of the bearing support device facing the groove.   A bearing support device for supporting a bearing, wherein a damping member is provided at a portion facing the bearing when the bearing is mounted, the rotation being mounted on the bearing and the bearing When the body is mounted, at least a part of the damping member has a portion that receives a load in the thrust direction, and complementary concave and convex grooves that are fitted to each other have a surface of the portion of the damping member that receives the thrust load A plurality of bearings are formed over the entire surface of the bearing support device facing the bearings, and each surface of the concave and convex grooves extends in a direction inclined with respect to the acting direction of the thrust load. Support device.   A rotating body mounted on a bearing, wherein the rotating body is provided with a damping member at a portion facing the bearing when mounted on the bearing, and the surface of the damping member faces the damping member. Complementary concavo-convex grooves that are fitted to each other are provided on the surface of the rotating body, and the concavo-convex grooves are relative to the damping member and the rotating body facing the damping member in the rotation direction of the bearing. A rotating body characterized by preventing the displacement of the rotating body.   It is a rotary body of Claim 28, Comprising: The said uneven groove | channel which mutually fits forms a space | gap, The rotary body characterized by the above-mentioned.   30. The rotating body according to claim 28, wherein at least a part of the damping member receives a load in a thrust direction when mounted on a bearing support device that supports the bearing via the bearing, A rotating body characterized in that concave and convex grooves are provided on the surface of a portion of a vibration damping member that receives the thrust load and on the surface of the rotating body facing it.   A rotating body mounted on a bearing, wherein the rotating body is provided with a damping member at a portion facing the bearing when mounted on the bearing, and the bearing support device supports the bearing via the bearing. And at least a part of the vibration damping member receives a load in the thrust direction, and complementary concave and convex grooves fitted to each other have a surface of the vibration damping member receiving the thrust load and the surface thereof. A plurality of rotations formed over the entire surface of the rotating body facing each other, and each surface of the concave and convex grooves extends in a direction inclined with respect to the acting direction of the thrust load. body.   A bearing having an outer circumferential surface and an inner circumferential surface, wherein a damping member is provided on at least one of the outer circumferential surface and the inner circumferential surface, the surface of the damping member facing the damping member. Complementary concavo-convex grooves that fit each other are provided on the surface, and the concavo-convex grooves prevent displacement in the rotational direction of the bearing relative to the vibration-damping member and the bearing facing the vibration-damping member. Bearing characterized by.   33. The bearing according to claim 32, wherein the concave and convex grooves fitted to each other form a gap.   33. The bearing according to claim 32, wherein at least a part of the damping member receives a load in a thrust direction when mounted on a bearing support device that supports the bearing and a rotating body is mounted. A bearing characterized in that a groove is provided on the surface of a portion of the vibration damping member that receives the thrust load and the surface of the bearing facing the groove.   33. The bearing according to claim 32, wherein the bearing is operated by applying a preload, wherein at least a part of the damping member has a portion that receives the preload, and the uneven groove receives the preload. A bearing provided on a surface of a portion and a surface of the bearing facing the portion.   A bearing having an outer peripheral surface and an inner peripheral surface, wherein a vibration damping member is provided on at least one of the outer peripheral surface and the inner peripheral surface, and mounted on a bearing support device that supports the bearing and mounted with a rotating body In this case, at least a part of the vibration damping member has a portion that receives a load in the thrust direction, and complementary concave and convex grooves that are fitted to each other face the surface of the portion of the vibration damping member that receives the thrust load and the bearing And a plurality of the concave and convex grooves are formed so as to extend in a direction inclined with respect to a direction in which the thrust load is applied. A bearing having an outer peripheral surface and an inner peripheral surface, wherein a vibration damping member is provided on at least one of the outer peripheral surface and the inner peripheral surface, and is operated with a preload applied thereto, wherein at least a part of the vibration damping member Has a portion that receives the preload, and a plurality of complementary concave and convex grooves that fit together are formed over the entire surface of the portion of the vibration-damping member that receives the preload and the surface of the bearing that faces the surface. The bearing according to claim 1, wherein the surface of each of the concave and convex grooves extends in a direction inclined with respect to a direction in which the preload acts.

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