JP4411979B2 - Bearing device - Google Patents

Description

  The present invention relates to a bearing device having a damping member on a peripheral surface.

In order to absorb various harmful vibrations generated in the vicinity of the bearing device, a vibration damping material may be interposed between the bearing device and an external member (housing or the like).
For example, in a ball bearing for wind instruments provided with inner and outer rings and rolling elements, a damping member made of a resin or the like having a relatively low elastic coefficient is provided on a raceway circumferential surface such as an outer circumferential surface of the outer ring or an inner circumferential surface of the inner ring. The technique to provide is known (refer patent document 1).
JP 2000-110844 (FIG. 2, FIG. 3, page 3)

However, when the vibration damping member is made of a member having poor heat resistance such as a resin, there is a problem that it cannot be installed at a part where the temperature becomes high. In addition, since the resin or the like has a relatively low rigidity, there is a problem that the rigidity of the bearing device is reduced.
Further, in the prior art, the method of fixing the vibration damping member on the raceway ring circumferential surface simply sandwiches the vibration damping member between the external member and the raceway ring circumferential surface of the bearing. Therefore, in order to firmly fix the bearing to the external member, it is necessary to make the interference between the bearing and the external member relatively large and press-fit strongly, but in this case, the residual compressive stress of the damping member increases. The vibration control effect will be reduced. On the other hand, if the residual compressive stress of the damping member is reduced to avoid a decrease in the damping effect, the bearing is likely to drop off from the external member due to the influence of vibration and the like.

  The present invention has been made in view of such a situation, and in a bearing device provided with a vibration damping member, heat resistance and rigidity are relatively high, and dropout is prevented while minimizing residual compressive stress of the vibration damping member. It aims at providing the bearing device which can be performed.

The bearing device of the present invention includes a race ring, an annular damping member made of a damping alloy and provided on the circumferential surface of the race ring, and a diameter of the damping member provided on the circumferential surface of the damping member. An end ring-shaped first ring-shaped member that prevents falling off in the direction, and a ring-shaped end ring-shaped second ring member that is fixed on the circumferential surface of the raceway and projects more radially than the vibration damping member; The bearing ring has a fixed groove for preventing the vibration damping member from moving in the axial direction, and the vibration damping member has the vibration damping member in the circumferential direction. A plurality of arc-shaped members formed by division, and installed in the fixed groove, and having an installation portion for installing the first ring- shaped member, A first gap is formed between the arc-shaped members adjacent to each other in the circumferential direction. Both end faces of the grayed member second gap formed by facing away from each other in the circumferential direction, characterized in that are provided so as to overlap in the circumferential direction with respect to the first gap.

  If it does in this way, since a damping member consists of damping alloys, heat resistance and rigidity will improve compared with the case where they consist of general resin etc. Since the damping member is divided in the circumferential direction, it can be installed in the fixed groove from the radial direction. Since the damping member is prevented from moving in the axial direction by the fixed groove on the bearing ring and does not fall off in the radial direction by the end ring-shaped first ring member, it is not strongly pressed into the outer case or the like. Will not fall off. Further, since both the first ring-shaped member and the second ring-shaped member are ring-shaped ends, they can be elastically deformed and installed from the radial direction, and the assembly of the bearing device is easy. Then, by engaging the ring-shaped member that protrudes in the radial direction with respect to the damping member with the outer case or the like, the bearing device does not fall off even if it is not strongly pressed into the outer case or the like.

  In the bearing device described above, the damping member may be divided in the axial direction. By dividing in the axial direction in addition to the circumferential direction, the contact surface between the divided vibration damping members increases, and the vibration damping effect is further improved by sliding on the contact surface.

  The contact surface between the divided vibration damping members may include a surface inclined with respect to the radial direction. In this way, the sliding surface can be widened, and particularly when a radial load is applied, sliding occurs between the inclined surfaces and deforms the damping member. Can be increased.

  The damping member may be composed of a plurality of types of damping alloys. In this case, it is possible to provide a vibration damping member that makes use of the characteristics of each alloy material, and the degree of freedom in designing the vibration damping member can be increased. As a result, for example, when there are a plurality of vibrating frequency regions (peaks), the vibration damping performance is improved by using a plurality of types of vibration damping alloys corresponding to each of these frequency regions, and the oil resistance is excellent. It is also possible to sandwich the material damping member with a material having a weak oil resistance.

  In the above bearing device, the bearing portion is a cylindrical roller bearing or a needle roller bearing, and the axial range of the contact portion between the damping member and the bearing ring is the contact portion between the roller and the raceway surface. It is good also as a structure containing the axial direction range. Cylindrical roller bearings and needle roller bearings are usually used in areas where little axial load is applied, and are used in a state where they are not strongly pressed into external members. Is preferably used. The vibration transmitted through the bearing device is transmitted through the contact portion between the rolling element (roller) and the raceway surface, and a damping member is provided in a range covering the axial existence range of the contact portion. As a result, the damping performance as the bearing device is further enhanced.

  Since a damping alloy is used as the damping member, heat resistance and rigidity are increased. Further, since the fixing groove and each ring-shaped member are used as the fixing means, the bearing device can be prevented from falling off while minimizing the residual compressive stress of the damping member and can be easily assembled. Furthermore, since the vibration damping member is divided in the circumferential direction, the vibration damping member can be installed in the fixed groove.

Embodiments of the present invention will be described below with reference to the drawings.
FIG. 1 is a cross-sectional view of a bearing device 1 for an automobile transmission according to a first embodiment of the present invention. The bearing device 1 has a cylindrical roller bearing 11 at the bearing portion. That is, the cylindrical roller bearing 11 includes a plurality of cylindrical rollers 2 as rolling elements arranged at substantially equal intervals in the circumferential direction, and an outer ring 3 as a bearing ring having a raceway surface 3a on which the cylindrical rollers 2 roll. The retainer 4 holds the arrangement of the cylindrical rollers 2 at substantially equal intervals in the circumferential direction. The bearing device 1 further includes an annular damping member 5 provided on the outer peripheral surface 3 b of the outer ring 3. The damping member 5 is made of a damping alloy such as an Fe—Al alloy, an Fe—Cr alloy, an Mn—Cu alloy, an Fe—Cr—Al alloy, a Ni—Ti alloy, and an Mg alloy.
A cylindrical roller bearing 11 portion of the bearing device 1 is attached to a transmission case 12 made of aluminum of a transmission via a damping member 5 and is externally fitted to a drive shaft 10 in the transmission. The shaft 10 is rotatably supported.

  The vibration damping member 5 is divided equally into a plurality of arc-shaped members in the circumferential direction, and the whole of these arc-shaped members forms an annular shape. 2 is a cross-sectional view taken along the line AA in FIG. 1. As shown in FIG. 2, the vibration damping member 5 includes arcuate members 51a to 54a divided into four equal parts in the circumferential direction. ing. That is, the vibration damping member 5 includes four arcuate members 51a to 54a. All of these 51a to 54a have the same shape. In FIG. 2, the cylindrical roller 2 and the cage 4 are not shown. In addition, the division | segmentation to the circumferential direction of the damping member 5 can be made into 2 or more division | segmentation, and when dividing | segmenting equally into the circumferential direction, it can divide into 2 or more division | segmentation.

  As shown in FIG. 1, a fixing groove 6 for preventing the axial movement of the vibration damping member 5 is provided on the outer peripheral surface 3 b side of the outer ring 3. That is, by an annular first flange 31 projecting radially outward on one axial end side of the outer ring 3 and an annular second flange 32 projecting radially outward on the other axial end side of the outer ring 3, A fixing groove 6 is formed on the outer peripheral surface 3 b of the outer ring 3. A damping member 5 is installed in the fixed groove 6.

  Inside the fixed groove 6, not only the damping member 5 but also the second ring-shaped member 8 is installed. The second ring-shaped member 8 is provided adjacent to the other axial end of the vibration damping member 5 and in contact with the second flange 32. The second ring-shaped member 8 is composed of a ring-shaped member having an end which can be elastically deformed so as to expand its diameter, such as a C ring or a snap ring, and is sandwiched between the vibration damping member 5 and the second flange 32. Yes. The second ring-shaped member 8 is installed in a gap between the vibration damping member 5 and the second flange 32. The damping member 5 is sandwiched between the first flange 31 and the second ring-shaped member 8 described above.

  As shown in FIG. 1, a circumferential groove 9 as an installation portion for installing the first ring-shaped member 7 is provided at the axial center position of the outer peripheral surface of the vibration damping member 5. And the end ring-shaped 1st ring-shaped member 7 is accommodated in this circumferential groove 9. FIG. This first ring-shaped member 7 is not an endless annular member but a so-called C-ring having an end ring shape (see an enlarged view in FIG. 2). When assembling the bearing device 1, the first ring-shaped member 7 is fitted into the circumferential groove 9 from the radially outer side while being elastically deformed so as to expand the diameter once. The elastic force (spring force) of the first ring-shaped member 7 prevents the damping member 5 divided in the circumferential direction from falling off radially outward.

Next, the shape of the arc-shaped members 51a to 54a, which are vibration damping members divided in the circumferential direction, will be described in detail. Hereinafter, although it demonstrates as a shape of the circular-arc-shaped member 51a, the shape of another circular-arc-shaped member is also the same.
FIG. 3 is a perspective view of the arcuate member 51a (52a to 54a). The arc-shaped member 51a is a member having an arc shape as a whole and having a constant thickness in the circumferential direction. The arcuate member 51a constitutes the radially inner side surface 15 constituting the inner circumferential surface (a part thereof) of the annular damping member 5 and the outer circumferential surface (a part thereof) of the damping member 5 similarly. A radially outer surface 16. Since the radius of curvature of the radially inner side surface 15 is substantially the same as the radius of curvature of the outer peripheral surface 3b of the outer ring 3, the annular damping member 5 that is an aggregate of these arc-shaped members 51a to 54a is: The inner peripheral surface comes into contact with the outer peripheral surface 3b of the outer ring 3, and as a result, the annular damping member 5 is fitted onto the outer ring 3 (see FIGS. 1 and 2).

  As shown in FIG. 3, the circumferential groove 9 described above is provided across the circumferential direction at the central position in the axial direction (width direction) of the radially outer surface 16 in the arc-shaped member 51 a. Therefore, in the vibration damping member 5 in which the arc-shaped members 51a to 54a are combined to form an annular shape, the circumferential groove 9 is continuously provided over the entire circumference in the circumferential direction.

The assembly procedure of the bearing device 1 is performed as follows.
First, arc-shaped members 51 a to 54 a constituting the vibration damping member 5 are arranged in an annular shape in the fixed groove 6 of the outer ring 3. These arc-shaped members 51 a to 54 a are arranged close to one end side in the axial direction so as to contact the first flange 31. Since these arc-shaped members 51a to 54a are divided, they can be installed in the fixed groove 6 from the radially outer side. Thus, by arranging the arc-shaped members 51a to 54a in an annular shape, the circumferential groove 9 is in an annularly continuous state.
Next, the first ring-shaped member 7 is fitted into the circumferential groove 9 from the radially outer side of the outer ring 3 and attached. Since the first ring-shaped member 7 is a C-ring, the first ring-shaped member 7 can be temporarily deformed so as to expand in diameter and can be fitted into the circumferential groove 9 from the radially outer side of the damping member 5. And the damping member 5 which consists of circular-arc-shaped members 51a-54a will be in the state pressed on the outer peripheral surface 3b by the elastic force of the 1st ring-shaped member 7. FIG.
Further, the second ring-shaped member 8 is installed in the gap between the vibration damping member 5 (51 a to 54 a) and the second flange 32 of the outer ring 3. Since the second ring-shaped member 8 is a snap ring, like the first ring-shaped member 7 described above, the second ring-shaped member 8 can be deformed so as to be expanded once and inserted into the gap from the radially outer side of the outer ring 3. it can.

In the bearing device 1 assembled as described above, the second ring-shaped member 8 is fixed on the outer peripheral surface 3b of the outer ring 3 by being sandwiched between the damping member 5 and the second flange 32, and It protrudes radially outward from the damping member 5. When the bearing device 1 is mounted on the mission case 12, the projecting portion 8 a is engaged with the mission case 12. (See FIG. 1).
The procedure for engaging the projecting portion 8a of the second ring-shaped member 8 projecting radially outward from the damping member 5 with the transmission case 12 is as follows. On the inner peripheral surface of the transmission case 12 to which the bearing device 1 is mounted, a ring groove 12a into which the protruding portion 8a of the second ring-shaped member 8 in the bearing device 1 is inserted is provided over substantially the entire circumference. . When the bearing device 1 is attached to the mission case 12, the bearing device 1 is fitted into the mission case 12 in a state where the second ring-shaped member 8 is elastically deformed so as to reduce the diameter. (When the bearing device 1 is attached to the transmission case 12 as shown in FIG. 1, there is a gap k that allows the diameter of the second ring-shaped member 8 to be reduced.) And the second ring-shaped member 8 is a ring. When the position of the groove 12a is reached, the diameter of the second ring-shaped member 8 is increased, and the protrusion 8a of the second ring-shaped member 8 is inserted into the ring groove 12a.
For example, when the second ring-shaped member 8 is a snap ring, as shown in FIG. 7, the end t of the snap ring can be inserted into the mission case 12 from the other end side of the mission case 12 and the bearing device 1. Is provided in the transmission case 12 with a notch 12b capable of accommodating the end point t. Then, the end point t is inserted into the notch 12b with the snap ring having a reduced diameter, and the snap ring is released and enlarged at the position of the ring groove 12a. 7 is a view of the vicinity of the notch 12b of the mission case 12 as seen from the other end side (right side in FIG. 1) of the mission case 12, and the description of the bearing device 1 is omitted.

The bearing device 1 of the first embodiment configured as described above has the following operational effects. Since the damping member 5 is made of a damping alloy, heat resistance and rigidity are improved as compared with a case of being made of a general resin or the like. Therefore, it is possible to provide a bearing device that can withstand the internal temperature of the transmission that is as high as about 150 ° C. The vibration control member 5 can effectively suppress vibration transmission between the drive shaft 10 and the transmission case 12.
Further, since the damping member 5 is divided in the circumferential direction, it can be installed in the fixed groove 6 from the radial direction. In addition, the vibration damping member 5 can be constituted by a small member by being divided, and even if it is a large-sized bearing, it is not necessary to make the vibration-damping member 5 a large-sized integral member. Become.

Since the damping member 5 is sandwiched by the fixing groove 6 (and the second ring-shaped member 8) on the race, the movement in the axial direction is prevented, and the radial direction is prevented by the first ring-shaped member 7. Since it is held from the outside, it does not move in the radial direction and the axial direction, and does not fall off from the outer ring 3. Furthermore, the protrusion 8 a of the second ring-shaped member 8 is engaged with the transmission case 12, so that the bearing device 1 does not drop from the transmission case 12. Therefore, it is not necessary to press-fit the bearing device 1 strongly into the transmission case 12 to prevent dropping. That is, the bearing device 1 can be fixed to the transmission case 12 by weak press-fitting or clearance fitting with a minimum interference. The damping alloy tends to reduce the damping effect when the residual compressive stress is high, but here, the damping member 5 can be used with the residual compressive stress being minimized or zero. The vibration control effect of 5 can be maximized.
Further, the bearing device 1 can be handled as a member that is not separated by the bearing device 1 alone because the cylindrical roller bearing 11 and the damping member 5 and the like are not separated in the state of the bearing device 1 alone.

  Since the damping member 5 is divided in the circumferential direction, it is possible to suppress an adverse effect due to a difference in linear expansion coefficient with the transmission case 12. The transmission case 12 is made of aluminum, and usually has a larger linear expansion coefficient than the vibration damping member 5 and the outer ring 3, so that a gap between the transmission case 12 and the bearing device 1 (vibration control member 5) is increased as the temperature rises. growing. In this case, the rotation shaft may be misaligned, and various bearing performances may be deteriorated, such as an increase in vibration and an increase in rolling resistance. However, since the vibration damping member 5 is divided in the circumferential direction, the thermal expansion in the radial direction is larger than that of the ring-integrated vibration damping member 5 that is not divided. The reason is as follows. In the ring-shaped integral damping member 5, the inner and outer diameters are both increased because the ring-shaped damping member 5 expands in a circumferential direction. However, when the vibration damping member 5 is divided in the circumferential direction, the vibration damping member 5 has a block shape, and thus expands to both the inner diameter side and the outer diameter side. As a result, the outer diameter of the bearing device 1 is increased. The increase in the gap between the inner diameter of the transmission case 12 (outer case) is suppressed. That is, when the vibration damping member 5 is divided in the circumferential direction, the increase in the gap due to the difference in the linear expansion coefficient is suppressed as compared with the case of the vibration damping member 5 that is not divided in the circumferential direction.

FIG. 4 is a cross-sectional view of the bearing device 1 according to the second embodiment of the present invention. In the following sectional views of FIGS. 4 to 6, only half of the bearing device 1 is shown from the central axis, and the remaining portions are not shown.
In the second embodiment, unlike the first embodiment, the vibration damping member 5 is divided (two divided) not only in the circumferential direction but also in the axial direction. That is, the damping member 5 is divided in the circumferential direction and also in the axial direction, and the first arc-shaped member 5a located on one end side in the axial direction and the second arc shape located on the other end side in the axial direction. Member 5b. The first arc-shaped member 5a and the second arc-shaped member 5b are members having the same shape, and each includes a circumferential groove 9 on the outer peripheral surface. Accordingly, there are a total of two circumferential grooves 9 as the vibration damping member 5, and two first ring-shaped members 7 made of a C ring are fitted and accommodated in these two circumferential grooves 9.

In this case, since the first arc-shaped member 5a and the second arc-shaped member 5b can slide on the contact surface s, the damping effect of the damping member 5 is further enhanced. In the bearing device 1 of the first embodiment described above, the damping performance is improved by the presence of the contact surface s generated by the circumferential division of the damping member 5, but the damping member 5 as in the second embodiment. Is divided in the axial direction, the area of the contact surface s becomes very large, so that the damping effect of the damping member 5 is further enhanced.
Further, by dividing in the axial direction, the axial width of each arcuate member constituting the damping member 5 is reduced, and the workability of the arcuate member is extremely increased.

  If the number of divisions in the axial direction is increased, not only the vibration damping effect is increased due to the increase of the contact surface s, but also the tolerance for the inclination between the bearing device 1 and the transmission case 12 is increased. That is, when the bearing device 1 is inclined with respect to the transmission case 12, the plurality of arcuate members arranged adjacent to each other in the axial direction change their postures so that the vibration damping member 5 as a whole is easily deformed. It becomes easy to follow the inclination of 1.

FIG. 5 is a cross-sectional view of the bearing device 1 of the third embodiment.
The vibration damping member 5 of the present embodiment is also divided in the circumferential direction, and is also divided into three in the axial direction. The first arcuate member 5a is disposed on one end side in the axial direction, and is disposed on the other end side in the axial direction. And a second arcuate member 5b and a third arcuate member 5c provided between these 5a and 5b. Therefore, the number of axial divisions is larger than that of the second embodiment divided into two in the axial direction, and the contact surface s is widened accordingly. Further, the contact surface s generated by the division in the axial direction includes not only a surface parallel to the radial direction as in the second embodiment described above but also an inclined surface s2 that is inclined with respect to the radial direction. By providing the inclined surface s2, the contact surface s can be made wider, and particularly when a radial load is applied, sliding occurs between the inclined surfaces s2 to deform the damping member 5. The vibration control effect can be further enhanced. The inclined surface s2 may be a flat surface or a curved surface.

  Further, in the third embodiment of FIG. 5, the vibration damping member 5 is prevented from falling off in the radial direction by only one first ring-shaped member 7, although it is divided into three in the axial direction. The third arcuate member 5c has a portion in which the axial width continuously decreases from the radially outer side to the inner side. Conversely, the first arc-shaped member 5a and the second arc-shaped member 5b have a portion in which the axial width continuously increases from the radially outer side to the inner side. As a result, the above-described inclined surface s2 is provided. In the inclined surface s2, the third arcuate member 5c is radially outward of the first arcuate member 5a and the second arcuate member 5b. Is supposed to be located. Therefore, by providing the circumferential groove 9 only in the third arcuate member 5c and installing the first ring-like member 7 in the circumferential groove 9, not only the third arcuate member 5c but also the first arcuate member 5a and the first arcuate member 5c. The two arcuate members 5b are prevented from falling off in the radial direction.

  Although common to the first to third embodiments described above, as shown in FIG. 4 representatively, the axial length L2 of the contact portion between the damping member 5 and the outer ring 3 is the same as the raceway surface 3a of the outer ring 3. The length of the contact portion with the cylindrical roller 2 is longer than the axial length L1. Further, the axial range H <b> 2 of the contact portion between the damping member 5 and the outer ring 3 includes the axial range H <b> 1 of the contact portion between the raceway surface 3 a of the outer ring 3 and the cylindrical roller 2. The vibration transmitted through the bearing device 1 is transmitted through the contact portion between the cylindrical roller 2 that is a rolling element and the raceway surface 3a. The vibration is suppressed to an axial range that covers the axial existence range of the contact portion. Since the member 5 is provided, the vibration damping performance as the bearing device 1 is further enhanced.

  The division of the damping member 5 in the circumferential direction is preferably equally divided in the circumferential direction. In this case, since the divided surfaces of the damping member 5 are evenly distributed in the circumferential direction, the uniformity in the circumferential direction is improved. Moreover, since the circular arc member which comprises the damping member 5 is shared, the assembly of the bearing apparatus 1 and management of the circular arc member become easy, and it contributes to cost reduction. A gap may be provided in the circumferential division position of the damping member 5, that is, a circumferential seam portion between the arcuate members, and a spacer may be provided in the gap. This spacer can also be a damping alloy.

  The damping member 5 may be composed of a plurality of types of damping alloys. This is easily configured by changing the material between the arcuate members formed by dividing the vibration damping member 5. In this case, different damping alloys may be used between the arc-shaped members arranged (divided) in the circumferential direction, or different damping alloys may be used between the arc-shaped members arranged (divided) in the axial direction. The axial direction and the circumferential direction may be different. When different damping alloys are used in the circumferential direction, for example, two types of damping alloys may be alternately arranged in the circumferential direction. In this way, the uniformity in the circumferential direction can be ensured while differentiating the two types of damping alloys in the circumferential direction.

  Further, by using a plurality of types of damping alloys, the damping member 5 can be made using the characteristics of each alloy material, and the degree of freedom in designing the damping member 5 can be increased. As a result, for example, when there are a plurality of vibrating frequency regions (peaks), the vibration damping performance can be improved by using a plurality of types of vibration damping members 5 corresponding to each of these frequency regions, or excellent in oil resistance. It is also possible to sandwich a damping member made of a material with a damping member made of a material having low oil resistance.

  As the first ring-shaped member 7 and the second ring-shaped member 8, an end-ring-shaped ring-shaped member that can be elastically deformed so as to be expanded (or contracted), such as a C ring or a snap ring, is used. it can. By using these members, when the bearing device 1 is assembled, it can be attached from the radial direction of the bearing device 1 after being elastically deformed once, so that the assembly of the bearing device 1 is facilitated.

  The bearing portion of the bearing device is preferably a cylindrical roller bearing or a needle roller bearing. Cylindrical roller bearings and needle roller bearings are usually used in areas where little axial load is applied, and are used in a state where they are not strongly pressed into external members. Is preferably used.

  In each of the above embodiments, the damping member 5 is provided on the outer circumferential surface of the outer ring 3, but when the bearing includes an inner ring, the damping member 5 may be provided on the inner circumferential surface of the inner ring. Needless to say. As an assembling method of the bearing device 1 in this case, the first ring-shaped member 7 and the second ring-shaped member 8 may be fitted from the radially inner side in a state where the first ring-shaped member 7 and the second ring-shaped member 8 are elastically deformed so as to be once reduced in diameter. Further, between the first flange 31 and the damping member 5 of the outer ring 3, between the second ring-shaped member 8 and the second flange 32, and between the second ring-shaped member 8 and the damping member 5. Of course, other members may be interposed therebetween.

  Moreover, in each said embodiment, although the 1st ring-shaped member 7 and the 2nd ring-shaped member 8 were made into a different body, you may make these common. For example, as in the fourth embodiment shown in FIG. 6, a ring-shaped member 20 in which the first ring-shaped member 7 and the second ring-shaped member 8 are integrated can be used. In this case, a step portion 21 is provided on the end surface on the other end side in the axial direction of the damping member 5 as an installation portion for installing the ring-shaped member. The axial thickness of the ring-shaped member 20 is substantially the same as the gap between the radial surface 21a of the stepped portion 21 and the second flange 32, and the ring-shaped member 20 is fitted in the gap. The ring-shaped member 20 prevents the vibration damping member 5 from dropping out radially outward, and prevents the vibration damping member 5 from moving toward the other end in the axial direction by contacting the radial surface 21a of the stepped portion 21. is doing. In this way, the first ring-shaped member 7 and the second ring-shaped member 8 may be integrated.

It is sectional drawing of the bearing apparatus which is 1st embodiment of this invention. It is sectional drawing in the AA line of FIG. 1, and its one part enlarged view. It is a perspective view of the circular-arc-shaped member which comprises a damping member. It is sectional drawing of the bearing apparatus which is 2nd embodiment of this invention. It is sectional drawing of the bearing apparatus which is 3rd embodiment of this invention. It is sectional drawing of the bearing apparatus which is 4th embodiment of this invention. It is a figure of the notch part for snap rings provided in the mission case.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Bearing apparatus 2 Cylindrical roller 3 Outer ring 3a Raceway surface 3b Perimeter surface (surrounding surface of a raceway ring)
4 Cage 5 Damping member 51a to 54a Arc-shaped member (divided damping member)
5a, 5b, 5c Arc-shaped members (divided vibration damping members)
6 fixing groove 7 first ring-shaped member 8 second ring-shaped member 9 circumferential groove (installation part)
11 Cylindrical roller bearing 21 Stepped part (installation part)
s contact surface s2 inclined surface (surface inclined with respect to radial direction)

Claims (5)

A ring-shaped damping member made of a raceway ring, made of a damping alloy and provided on the circumferential surface of the raceway ring, and a radial damping of the damping member provided on the circumferential surface of the damping member is prevented. A bearing device comprising: an end ring-shaped first ring-shaped member; and a ring-shaped end ring-shaped second ring member that is fixed on a peripheral surface of the raceway and projects more radially than the vibration damping member. There,
The bearing ring has a fixing groove for preventing the vibration damping member from moving in the axial direction,
The vibration damping member is composed of a plurality of arc-shaped members obtained by dividing the vibration damping member in the circumferential direction, and is installed in the fixed groove, and an installation portion for installing the first ring-shaped member a has,
Among the plurality of arcuate members, a first gap is formed between the arcuate members adjacent to each other in the circumferential direction,
A second gap formed by opposing both end faces of the first ring member away from each other in the circumferential direction is provided so as to overlap the first gap in the circumferential direction. Bearing device.   The bearing device according to claim 1, wherein the damping member is divided in an axial direction.   The bearing device according to claim 1, wherein a contact surface between the divided vibration damping members includes a surface inclined with respect to a radial direction.   The bearing device according to claim 1, wherein the damping member is made of a plurality of types of damping alloys.   The bearing portion is a cylindrical roller bearing or a needle roller bearing, and the axial range of the contact portion between the damping member and the raceway includes the axial range of the contact portion between the roller and the raceway surface. The bearing device according to any one of claims 1 to 4, wherein

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