JP2012145181A - Thrust washer and bearing - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a thrust washer that can stably be assembled into an inner ring of a bearing by using a simple assembling device without using a pressure-insertion device, and can stably prevent the wear of an inner ring end face or the like in terms of rigidity for a long period of time, and a bearing using such a thrust washer.SOLUTION: The thrust washer which is attached to the inner ring 21 of the rolling bearing, and prevents the wear of one axial end face 21b of the inner ring 21 and an end face of a mating member which opposes the axial end face 21b comprises; a disk-shaped body 30a which faces one axial end face 21b of the inner ring 21; and a rectangular cylindrical collar 30b which is protrusively formed at the external peripheral edge of the disk-shaped body 30a, and externally covers one axial end of the inner ring 21. At the collar 30b, there is formed a hanging part 32 which is protruded to the inside diameter side from the inside diameter face, and hung to a circumferential groove 50 formed at the outer diameter surface 25a of the inner ring 21. The collar 30b is divided by a notch 40.

Description

  The present invention relates to a bearing such as a tapered roller bearing or a tandem angular ball bearing for supporting a pinion shaft of an automobile differential, and a thrust washer used for such a bearing.

  Generally, as shown in FIGS. 10 and 11, the tapered roller includes an inner ring 1 having a tapered raceway surface 1a on an outer peripheral surface, an outer ring 2 having a tapered raceway surface 2a on an inner peripheral surface, and both of these raceways. A plurality of tapered rollers 3 as rolling elements incorporated between the wheels 1a and 2a, and a cage 4 that holds each tapered roller 3 in a freely rollable manner. A large collar 5 and a small collar 6 are integrally formed at the end of the inner ring 1 on the large diameter side and the end of the small diameter side so that the tapered roller 3 and the retainer 4 do not fall off the inner ring 1.

  Further, the tapered roller bearing configured as described above has an inner ring 1 fitted to a mating member (for example, a differential drive pinion shaft or a differential gear case), and a large-diameter end face 1b (hereinafter simply referred to as a “ring wheel”). Appropriate bearing preload is provided by bringing the inner ring end surface (also referred to as the inner ring end face) into contact with the end face of the flange portion extending in the radial direction from the counterpart member (hereinafter also referred to simply as the flange end face) and pressing the outer ring 2 toward the flange end face is doing. By applying an appropriate bearing preload in this manner, the fatigue life of the tapered roller bearing is extended, and the meshing of the gear of a gear unit such as a differential is improved to prevent troubles such as gear chipping.

  However, when a high torque is input to the gear device, the mating member may be twisted, and stick slip (slip) may occur between the inner ring end face 1b and the flange end face. At this time, along with the occurrence of stick-slip noise, wear occurs on the inner ring end face and the flange end face. When the inner ring end surface 1b and the flange end surface are thus worn, the inner ring 1 is separated from the outer ring 2 and causes a decrease in bearing preload.

  Thus, as a technique for suppressing the wear of the inner ring end face and the flange end face so that the bearing preload does not decrease, for example, there is a tapered roller bearing (rolling bearing) disclosed in Patent Document 1 below. As shown in FIG. 10, this tapered roller bearing has a washer 8 interposed between both end faces in order to prevent wear between the inner ring end face 1b and the flange end face.

  The washer 8 includes a disc-shaped washer main body 8a that abuts against the inner ring end face 1b, and a short cylindrical portion 8b that protrudes from the outer peripheral edge of the washer main body 8a. The short cylindrical portion 8 b is externally fitted to the large collar 5 of the inner ring 1. That is, the washer 8 is integrated with the inner ring 1 by press-fitting the short cylindrical portion 8 b to the outer peripheral surface of the inner ring large collar 5.

  By the way, when the washer 8 is used to suppress the wear of the inner ring end face 1b and the flange end face, as described above, the inner ring 1 and the washer 8 are integrated in advance so that the tapered roller bearing can be used as a mating member. It is also very important from the viewpoint of improving the workability when transporting to the assembly process or when actually assembling the both after transporting to the assembly process.

  On the other hand, however, if the washer 8 is press-fitted into the inner ring 1 to integrate them, it is essential to strictly manage the dimensional tolerances of the washer 8 and the inner ring 1. This is because if the dimensional tolerance between the two is not strictly controlled, there is a problem that the washer 8 is easily detached from the inner ring 1 without an appropriate fixing force acting between them.

  Therefore, when the washer 8 and the inner ring 1 are integrated by press fitting as described above, for example, the inner peripheral surface of the short cylindrical portion 8b of the washer 3 or the outer peripheral surface of the large collar 5 of the inner ring 1 is ground. Therefore, it is necessary to adjust the dimensions of both of them separately, resulting in a problem that the processing cost increases.

  Moreover, in the case of press-fitting, even if the dimensional tolerance between the washer 8 and the inner ring 1 can be managed with high accuracy, the center axes of the two are accurately aligned during press-fitting and the positional relationship is maintained. Therefore, it is necessary to press-fit the washer 8 into the inner ring 1. Therefore, the work of assembling the washer 8 and the inner ring 1 becomes very troublesome and complicated, and there arises a problem that the production efficiency is remarkably lowered.

  Therefore, as shown in FIG. 11, the engagement recess 10 is provided on the outer diameter surface of the inner ring 1, that is, the outer diameter surface of the large collar 5, and the engagement recess 10 is engaged with the outer peripheral edge of the washer 8. As shown in FIG. 12, a claw portion 8c having an engaging convex portion 11 is provided at a predetermined pitch (90 ° pitch in the example) along the circumferential direction (Patent Document 2).

  11 and FIG. 12, the engaging convex portion 11 of the claw portion 8c of the washer 8 is engaged with the engaging concave portion 10 on the outer diameter surface of the inner ring 1, and the engaging convex portion The part 11 is hooked on the engaging recess 10. For this reason, it is possible to have a loose fit without bringing the engaging convex portion 11 into close contact with the engaging concave portion 10, and the washer 8 is not press-fitted into the inner ring 1.

  That is, it is not necessary to tightly fit the inner diameter surface of the short cylindrical portion 8 b of the washer 8 to the outer diameter surface of the large collar 5 of the inner ring 1. This allowed the washer to be held at a level of turning finish tolerance.

JP 2002-323049 A JP 2009-299845 A

  However, in the one shown in FIGS. 11 and 12, the engaging recess 10 is a circumferential groove, and therefore, slippage occurs between the inner ring 1 and the washer 8 due to the twist of the pinion shaft. In such a case, since the claw part 8c is inferior in strength, the claw part 8c may be damaged. Further, even when the engaging convex portion 11 is loosely engaged with the engaging concave portion 10, when the engaging convex portion 11 is fitted to the engaging concave portion 10, the diameter of the claw portion 8c is increased. The claw portion 8c may be damaged during the engaging operation. Furthermore, in order to shape the shape of the claw portion 8c by press working or the like, it is necessary to secure necessary dimensions. That is, there may be a case where sufficient dimensions cannot be secured on the other side (the outer diameter surface of the inner ring large collar). In such a case, there is a possibility that the catch will not be established.

  The problem of the present invention is that it can be stably incorporated into the inner ring of the bearing with a simple assembling device without using a press-fitting device, and further, wear of the inner ring end face and the like can be prevented over a long period of time in a stable manner. It is an object of the present invention to propose a thrust washer and a bearing using such a thrust washer.

  A thrust washer according to the present invention is a thrust washer that is attached to an inner ring of a rolling bearing and prevents wear of one axial end face of the inner ring and a mating member end face facing the axial end face. A disc-shaped main body facing the direction end surface, and a short cylindrical collar projecting on the outer peripheral edge of the disc-shaped main body and fitting one axial end of the inner ring, the inner diameter of the collar A hook portion that protrudes to the side and hooks into a circumferential groove formed on the outer diameter surface of the inner ring is provided, and the collar portion is divided by a notch portion.

  In the thrust washer of the present invention, the disk-shaped main body faces the one axial end surface of the inner ring, so that the disk-shaped main body is between the axial end surface and the end surface of the mating member facing the axial end surface. Will be intervened. In addition, the hook portion is caught in the circumferential groove of the inner ring by externally fitting one axial end portion of the inner ring with the short cylindrical flange. As a result, the thrust washer can be attached to the inner ring. Further, since the catch structure of the catch portion is adopted, the fit between the outer diameter surface of the large collar of the inner ring and the inner diameter surface of the collar portion may be relatively loose.

  By the way, when the short cylindrical collar portion is externally fitted to the axial end portion of the inner ring, it is necessary to increase the diameter of the collar portion in order to have the catch portion. However, since this thrust washer is provided with a notched part for dividing the collar part in the short cylindrical collar part, the collar part is constituted by a plurality of arcuate bodies. For this reason, each arcuate body is deformed (expanded in diameter), and can be easily fitted on the axial end of the inner ring.

  It is preferable that 3 to 8 hooks are arranged at a predetermined pitch along the circumferential direction. If it is less than three, there are few catching parts and the state of incorporation into the inner ring becomes unstable. On the other hand, when the number is nine or more, the number of hooks is excessively increased, the manufacturing mold becomes complicated, and the manufacturing cost increases.

  The same number of hooks and notches can be provided. By providing the notch portion, the flange portion is divided, and a plurality of arcuate bodies constituting the flange portion are formed. For this reason, in order to obtain stable incorporation, each arcuate body requires at least one catching portion. Therefore, if the same number of hooks and notches are provided, the hooks can be provided on each arcuate body. That is, if two notches are formed, two arcuate bodies are formed, and a hook part can be provided on each arcuate body.

  It is preferable to provide a relief portion that is not in contact with the hook portion when the hook portion is engaged with the circumferential groove on the other axial end face side of the circumferential groove of the inner ring. By providing such an escape portion, it is possible to prevent the hook portion from interfering with the inner ring in a state where the hook portion is hooked in the circumferential groove.

  The notch bottom of the notch is preferably rounded. Thereby, the stress concentration at the time of elastic deformation of each arcuate body at the time of hooking the hook portion on the circumferential groove can be alleviated. Moreover, it is preferable to set the circumferential notch width of a notch part to 2 mm-20 mm. If it is less than 2 mm, the curvature radius of the notch bottom of the notch is small, and the relaxation of stress concentration is reduced. Moreover, when it exceeds 20 mm, the rigidity of the whole collar part will fall.

  It is preferable to set the plate thickness of the disc-shaped main body and the collar portion to 0.3 mm to 0.8 mm. If the plate thickness is less than 0.3 mm, it is too thin and the formability deteriorates. On the other hand, if it exceeds 0.8 mm, the plate thickness becomes large, the rigidity becomes excessively large, and the assemblability deteriorates.

  The protrusion amount from the inner diameter surface of the hook part of the hook part can be set to plus or minus 0.2 mm with respect to the plate thickness of the disk-shaped main body and the hook part. If it is less than minus 0.2 mm, the amount of protrusion may be small, and the amount of catch may not be ensured. On the other hand, if the thickness exceeds 0.2 mm, the protruding amount becomes too large, and the deformation amount of the heel portion at the time of assembling becomes large, which may damage the heel portion. By the way, the hook portion is formed by press working or the like. For this reason, in order to form a catching portion having a size protruding amount, it is necessary to make the plate thickness of the collar portion relatively small. As described above, when the plate thickness is small, the strength of the collar portion is reduced.

  It is preferable that the clearance between the hook portion and the groove bottom of the circumferential groove is −0.3 mm to +0.5 mm. As the catching portion, a clearance may be provided between the circumferential groove and the groove bottom, or a clearance may not be provided. If the amount of interference is greater than -0.3mm, an excessive force will be applied to the hooked part during installation. Conversely, if the amount of clearance exceeds + 0.5mm, the clearance will become too large and the circumferential groove Groove depth becomes large.

  You may make it provide the cover part which covers the inner ring | wheel outer-diameter surface of the anti-disk-shaped main-body part side rather than the anti-disk-shaped main body side edge of the circumferential groove in a collar part. By providing such a covering portion, it is possible to prevent the end portion (the end portion on the side of the anti-disk-shaped main body portion) from entering the circumferential groove when it is attached to the inner ring (when assembled).

  A nitride layer is preferably provided on the surface. Here, the nitriding layer is a layer formed by nitriding treatment, and nitriding treatment is a surface in which nitrogen is immersed in a metal surface in order to improve the wear resistance and corrosion resistance of steel products. It is the process of curing.

  The material can be SPCC or S60CM. SPCC is a relatively inexpensive material and has excellent wear resistance. S60CM is a relatively expensive material, but is superior in wear resistance.

  The rolling bearing can be applied to various types such as a tapered roller bearing, a tandem angular ball bearing, or an angular ball bearing.

  The bearing of the present invention includes an inner ring, an outer ring, a plurality of rolling elements interposed between the inner ring and the outer ring, and a cage that holds the rolling elements, and wear resistance at the end of the inner ring. This is a bearing equipped with a washer having the above, and the thrust washer is used as the washer.

  In the thrust washer of the present invention, the disc-shaped main body is interposed between the axial end surface and the mating member end surface facing the axial end surface, and wear between the axial end surface and the mating member end surface can be prevented. In addition, the thrust washer can be attached to the inner ring by hooking the catching portion in the circumferential groove of the inner ring, and it can be incorporated into the bearing inner ring with a simple assembling device without requiring a press-fitting device. In addition, by providing a notch that divides the collar, it can be easily fitted on the axial end of the inner ring, and as a hook in the circumferential groove, It can be configured by a hook portion provided on the short cylindrical collar, and is stable in strength. In other words, this thrust washer is formed by partially cutting a circular pipe structure, has high rigidity and strength, and can prevent damage during installation and use.

  In addition, since the fit between the outer diameter surface of the inner ring large collar and the inner diameter surface of the collar may be relatively loose, it is not necessary to strictly manage the tolerance of the inner diameter surface of the collar, and the inner ring large collar The outer diameter surface of can be turned and can be manufactured at low cost.

  Furthermore, this thrust washer is composed of a disc-shaped body and a short cylindrical collar, has a simple shape, and can be easily pressed without using complicated metal pressing (for example, blank punching → catching) Part processing → drawing processing). For this reason, inexpensive manufacturing is possible, and the degree of freedom in design increases.

  Providing three to eight hooks enables stable assembling of the thrust washer. By providing the same number of hooks and notches, stable assembling and stable hooking can be obtained.

  By providing the escape portion, excessive force on the catch portion does not act, and damage to the catch portion can be effectively prevented. By making the notch bottom of the notch into a round shape, stress concentration during assembly can be alleviated and durability can be improved. In particular, by setting the width of the notch to 2 mm to 20 mm, the stress concentration can be relaxed stably and the catch of the catch on the circumferential groove is stabilized.

  By setting the plate thickness to 0.3 mm to 0.8 mm, it is possible to improve moldability and incorporation. If the amount of protrusion of the catching portion is set to plus or minus 0.2 mm with respect to the plate thickness, the catching of the catching portion is stabilized and the strength of the catching portion is not reduced.

  By setting the clearance between the catching part and the groove bottom of the circumferential groove to be -0.3 mm to +0.5 mm, an excessive force does not act on the catching part at the time of assembly, and the catching part can be prevented from being damaged. Strength reduction can be prevented.

  By providing the covering portion, it is possible to prevent the end portion (the end portion on the side of the anti-disc-shaped main body portion side) from entering the circumferential groove and to effectively prevent damage to the flange portion.

  By providing the nitride layer, wear during bearing operation can be effectively prevented.

  SPCC or S60CM can be used. For example, SPCC can be selected when the use conditions are mild, and S60CM can be selected when SPCC cannot withstand use. In this way, the material can be selected in consideration of the intended use.

  It can be applied to various types of bearings, and this thrust washer is excellent in versatility.

  Moreover, in the bearing of the present invention, it is possible to prevent the occurrence of stick-slip noise and the wear of the inner ring end face and the like, and provide a bearing excellent in the ability to incorporate a thrust washer.

It is principal part sectional drawing of the tapered roller bearing incorporating the thrust washer of this invention. It is a principal part expanded sectional view of the said tapered roller bearing. It is a principal part expanded sectional view of the inner ring | wheel of the said tapered roller bearing. It is a top view of the thrust washer of this invention. It is sectional drawing of the said thrust washer. The said thrust washer is shown, (a) is a principal part expanded sectional view, (b) is A arrow directional view of the said (a). It is an expanded view of the collar part of the said thrust washer. It is principal part sectional drawing of the angular ball bearing incorporating the thrust washer of this invention. It is principal part sectional drawing of the tandem-type angular ball bearing incorporating the thrust washer of this invention. It is principal part sectional drawing of the tapered roller bearing incorporating the conventional thrust washer. It is principal part sectional drawing of the tapered roller bearing incorporating the other conventional thrust washer. FIG. 13 is a side view of the tapered roller bearing of FIG. 12.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings.

  FIG. 1 is a cross-sectional view of an essential part of a rolling bearing according to the present invention. This rolling bearing is a tapered roller bearing, and includes an inner ring 21 having a tapered raceway surface 21a on an outer peripheral surface and a tapered raceway on an inner peripheral surface. The outer ring | wheel 22 which has the surface 22a, the some tapered roller 23 as a rolling element integrated between these both track surfaces 21a and 22a, and the holder | retainer 24 which hold | maintains each tapered roller 23 so that rolling is possible are provided. A large collar 25 and a small collar 26 are integrally formed at the end of the inner ring 21 on the large diameter side and the end of the small diameter side so that the tapered roller 23 and the cage 24 do not fall off the inner ring 21.

  A thrust washer 30 is attached to the inner ring 21. As shown in FIGS. 4 and 5, the thrust washer 30 is composed of a disc-shaped main body 30a having a center hole 31 and a short cylindrical collar portion 30b protruding from the outer peripheral edge of the disc-shaped main body 30a. The thrust washer 30 (that is, the disk-shaped main body 30a and the flange portion 30b) can be made of, for example, a cold-rolled steel plate such as SPCC or a carbon steel such as S60CM. The plate thickness T is set to about 0.3 mm to 0.8 mm.

  The hook portion 30b is provided with a hook portion 32 that protrudes toward the inner diameter side. As shown in FIGS. 6 (a) and 6 (b), the catch portion 32 includes a circular protrusion 33. That is, the concave portion 34 is formed on the outer diameter surface 35 of the flange portion 30b, and the concave portion 34 is formed, thereby forming a circular projection portion 33 protruding toward the inner diameter side. In this case, the protruding amount of the hook portion 32 (dimension from the inner diameter surface 36 of the flange portion 30b to the bottom 32a of the hook portion 32) B is about plus or minus 0.2 mm of the plate thickness T.

  Moreover, the hook part 32 is provided in the axial direction intermediate part of the collar part 30b. For this reason, as shown in FIG. 2, the cover part 37 extended in parallel with respect to the outer-diameter surface 25a of the large collar 25 of the inner ring | wheel 21 is provided in the anti-disc-shaped main body side rather than the hook part 32.

  As shown in FIG. 4, four hook portions 32 are formed at a pitch of 90 degrees along the circumferential direction. Moreover, in the collar part 30b, the notch part (slit) 40 is provided between the hook parts 32 and 32 adjacent to the circumferential direction. That is, four slits 40 are also formed at a pitch of 90 degrees along the circumferential direction. For this reason, the collar part 30b is parted by the slit 40, and four arcuate bodies 41 are formed.

  As shown in FIG. 7, the slit 40 has a width dimension (circumferential cutout width) W set to about 2 mm to 20 mm. Further, the slit 40 reaches the anti-disc-shaped main body, and its bottom portion 40a has a round shape.

  And the circumferential groove | channel 50 is formed in the outer diameter surface 25a of the large collar 25 of the inner ring | wheel 21, as shown in FIG. 2 and FIG. In the bottom surface 51 of the circumferential groove 50, one axial end surface of the inner ring 21, that is, the large-diameter side axial end surface 21b side is an arcuate portion 51a, and the track surface 21a side is a tapered surface 51b. When the radius of curvature of the arc portion 51a is R1 (see FIG. 3) and the radius of curvature of the hooking portion 32 is R2 (see FIG. 6A), R1> R2. In this case, the inclination angle θ of the tapered surface 51b is, for example, about 30 ° to 50 °, and the circumferential depth D is about 0.4 mm to 0.8 mm.

  For this reason, when the thrust washer 30 is mounted on the inner ring 21, as shown in FIG. 2, the disc-shaped main body 30a corresponding to the axial end surface 21b on the large diameter side of the inner ring 21 contacts the axial end surface 21b. In this state, the catch portion 32 engages with the circumferential groove 50 in a loose fit. In other words, the hook portion 32 is caught in the circumferential groove 50. Further, in this hooked state, the tapered surface 51 b of the circumferential groove 50 becomes an escape portion 55 that does not come into contact with the hook portion 32.

  In this state, a gap 60 is provided between the bottom deepest portion (groove bottom) 52 of the circumferential groove 50 and the catch portion 32, and the flange portion extends from the opening edge 53 of the circumferential groove 50 on the side opposite to the disc-like body. The dimension (covering amount E) to the edge 37a of the covering part 37 of 30b is, for example, about 0.2 mm to 1.5 mm. Further, a gap 59 is provided between the inner diameter surface 36 of the collar portion 30 b and the outer diameter surface 25 a of the large collar 25 of the inner ring 21. The clearance dimension F of the clearance 59 is, for example, about 0.005 mm to 0.2 mm.

  By the way, in this embodiment, although the clearance gap 60 is provided between the bottom deepest part 52 of the circumferential groove | channel 50 and the catch part 32, in order to stabilize a catch, such a clearance gap 60 does not need to be provided. . That is, the gap amount C of the gap 60 is changed from −0.3 mm (a state where there is no gap 60 and interference) to +0.5 mm (a state where the gap 60 is provided).

  Next, a method of mounting the thrust washer 30 configured as described above on the inner ring 21 will be described. Assuming that the axial center of the thrust washer 30 and the axial center of the inner ring 21 are aligned, the thrust washer 30 is moved closer to the inner ring 21 from the larger diameter side of the inner ring 21, and the flange portion 30 b is moved to the outer diameter of the larger collar 25 of the inner ring 21. It will be incorporated so as to fit on the surface 25a. At this time, since the inner diameter dimension of the catching portion 32 is smaller than the outer diameter dimension of the outer diameter surface 25a of the large collar 25, when the collar section 30b is assembled, the collar section 30b is elastically expanded in diameter. With the portion 32 corresponding to the circumferential groove 50, the expanded state is restored from the expanded state by the elastic restoring force of the flange portion 30b. As a result, the hook portion 32 of the flange portion 30b is hooked in the circumferential groove 50.

  By the way, since the collar part 30b is divided by the notch part 40 and is composed of a plurality (four in the embodiment) of arcuate bodies 41, each arcuate body 41 is deformed (in this incorporation) ( And can be easily fitted on the end of the inner ring 21 in the axial direction.

  Further, by applying a force in the direction (axially outward) of the thrust washer 30 away from the inner ring 21 from the state shown in FIG. 2, the hook portion 32 is guided by the arc portion 51 a of the circumferential groove 50. Each arcuate body 41 is deformed (expanded in diameter), and the hook portion 32 escapes from the circumferential groove 50, and the hook state is released. The thrust washer 30 can be removed from the inner ring 21 by further pulling out the thrust washer 30 from the released state.

  In the thrust washer of the present invention, the disc-shaped main body 30a is interposed between the axial end surface 21b and the mating member end surface facing the axial end surface 21b, and wear between the axial end surface 21b and the mating member end surface can be prevented. Moreover, the thrust washer 30 can be attached to the inner ring 21 by the hook portion 32 being hooked in the circumferential groove 50 of the inner ring 21, and the bearing inner ring 21 can be mounted with a simple built-in device without requiring a press-fitting device. Can be incorporated into. Further, by providing the notch 40 for dividing the flange 30b, it can be easily fitted on the end of the inner ring 21 in the axial direction. It can be constituted by the hook portion 32 provided in the short cylindrical collar 30b instead of the portion, and is stable in strength. In other words, this thrust washer is formed by partially cutting a circular pipe structure, has high rigidity and strength, and can prevent damage during installation and use.

  Further, since the fitting between the outer diameter surface 25a of the large collar 25 of the inner ring 21 and the inner diameter surface 36 of the collar portion 30b may be relatively loose, it is not necessary to strictly manage the tolerance of the inner diameter surface 36 of the collar portion 30b. Moreover, the outer diameter surface 25a of the large collar 25 of the inner ring 21 may be turned and manufactured at a low cost.

  Further, this thrust washer is composed of a disc-shaped main body 30a and a short cylindrical flange 30b, has a simple shape, and can be easily pressed without using complicated metal pressing (for example, blank blanking). → Hooking part processing → drawing) For this reason, inexpensive manufacturing is possible, and the degree of freedom in design increases.

  Further, in this thrust washer 30, since the catch portion 32 is hooked in the circumferential groove 50 of the inner ring 21, when the thrust washer itself is worn, it can be easily removed from the inner ring 21, and a new The thrust washer 30 can be replaced. That is, even if the bearing to which the thrust washer 30 is mounted is used for a long period of time, no wear is caused between the axial end surface 21b and the mating member end surface facing the axial end surface 21b.

  Providing the plurality of hooks 32 enables the thrust washer 30 to be stably assembled. In this case, the number of hooks 32 is preferably 3 to 8. If it is less than three, there are few catching parts and the state of incorporation into the inner ring 21 becomes unstable. In addition, if the number is nine or more, the number of the catching portions 32 becomes too large, the manufacturing mold becomes complicated, and the manufacturing cost increases.

  By providing the same number of the hook portions 32 and the notch portions 40, the flange portion is divided to form a plurality of arcuate bodies constituting the flange portion 30b. For this reason, in order to obtain stable incorporation, each arcuate body 41 requires at least one hook portion 32. Therefore, if the same number of the hooks 32 and the notches 40 are provided, the hooks 32 can be provided on each arcuate body 41. That is, if two notches 40 are formed, two arcuate bodies 41 are formed, and the hooks 32 can be provided on each arcuate body 41. For this reason, stable integration and stable hooking can be obtained.

  By providing the escape portion 55, it is possible to prevent interference of the hook portion 32 with the inner ring 21 in a state where the hook portion 32 is hooked in the circumferential groove. As a result, an unreasonable force does not act on the catch portion 32, and damage to the catch portion can be effectively prevented. By making the notch bottom 52 of the notch 40 into a round shape, stress concentration during assembly can be alleviated and durability can be improved. In particular, when the width dimension of the notch 40 is 2 mm to 20 mm, the stress concentration can be relaxed stably, and the catch of the catch 32 on the circumferential groove 50 is stabilized. If it is less than 2 mm, the curvature radius R of the notch bottom part 52 of the notch part 40 is small, and relaxation of stress concentration is reduced. Moreover, if it exceeds 20 mm, the rigidity of the whole collar part 30b will fall.

  By setting the plate thickness to 0.3 mm to 0.8 mm, it is possible to improve moldability and incorporation. If the plate thickness is less than 0.3 mm, it is too thin and the formability deteriorates. On the other hand, if it exceeds 0.8 mm, the plate thickness becomes large, the rigidity becomes excessively large, and the assemblability deteriorates.

  If the amount of protrusion of the hook portion 32 is set to plus or minus 0.2 mm with respect to the plate thickness, the hook of the hook portion 32 is stabilized and the strength of the hook portion 32 is not reduced. If it is less than minus 0.2 mm, the amount of protrusion may be small, and the amount of catch may not be ensured. Moreover, if it exceeds plus 0.2 mm, the protrusion amount becomes too large, and the deformation amount of the collar part 30b at the time of assembling becomes large, which may damage the collar part 30b. By the way, the hook portion 32 is formed by press working or the like. For this reason, in order to form the catching portion 32 having a large protruding amount, it is necessary to make the plate thickness of the flange portion 30b relatively small. As described above, when the plate thickness is small, the strength of the flange portion 30b is lowered.

  By setting the clearance between the catching portion 32 and the groove bottom 51 of the circumferential groove 50 to −0.3 mm to +0.5 mm, an excessive force does not act on the catching portion 32 at the time of assembly, and the catching portion 32 is prevented from being damaged. In addition, the strength reduction of the inner ring 21 can be prevented. If the amount of interference is greater than -0.3 mm, an excessive force will be applied to the hook 32 during assembly. Conversely, if the amount of clearance exceeds +0.5 mm, the clearance will become too large and the circumferential groove The groove depth of 50 becomes large.

  By providing the cover portion 37, when the inner ring is mounted (assembled), it is possible to prevent the end portion (the end portion on the side of the anti-disk-shaped main body portion) from entering the circumferential groove 50 into the flange portion 30b. The damage of 30b can be effectively prevented.

  A nitride layer is preferably provided on the surface. Here, the nitriding layer is a layer formed by nitriding treatment, and nitriding treatment is a surface in which nitrogen is immersed in a metal surface in order to improve the wear resistance and corrosion resistance of steel products. It is the process of curing. Thus, by providing the nitride layer, it is possible to effectively prevent wear during bearing operation.

  SPCC or S60CM can be used. For example, SPCC can be selected when the use conditions are mild, and S60CM can be selected when SPCC cannot withstand use. In this way, the material can be selected in consideration of the intended use.

  By the way, in the said embodiment, although the rolling bearing was a tapered roller bearing, the angular ball bearing (single row angular contact ball bearing) as shown in FIG. 8, the tandem type angular contact ball bearing shown in FIG. 9, etc. may be sufficient. .

  That is, the angular ball bearing shown in FIG. 8 has balls (balls) 63 as a plurality of rolling elements interposed between the raceway surfaces 61 a and 62 a of the inner ring 61 and the outer ring 62, and a cage 64 that holds these balls 63. It is provided. In this case, a straight line L connecting the contact points of the balls 63 with the inner ring 61 and the outer ring 62 has a certain angle (contact angle). For this reason, a radial load and an axial load in one direction can be applied.

  The inner ring 61 is also provided with a thrust washer 30 as in the bearing shown in FIG. That is, the circumferential groove 50 is formed in the outer diameter surface 66 on the large diameter side of the inner ring 61, and the flange portion 30b of the thrust washer 30 is externally fitted to the large diameter portion of the inner ring 61, whereby the thrust washer is inserted into the circumferential groove 50. The hook part 32 of the 30 collar part 30b is hooked.

9 includes an inner ring 71 having raceway surfaces 71a and 71b, an outer ring 72 having double-row raceway surfaces 72a and 72b corresponding to the raceway surfaces 71a and 71b of the inner ring 71, and Between the raceway surfaces 71a, 71b, 72a, 72b of each row of the inner ring 71 and the outer ring 72, double rows of ball groups 73a, 73b interposed with different pitch circle diameters, and balls of the ball groups 73a, 73b ( Ball) 76 and retainers 74 and 75.
The straight lines L1 and L2 connecting the contact points of the balls (balls) 76 of the ball groups 73a and 73b and the inner ring 71 and the outer ring 72 have a certain angle (contact angle).

  Also in this case, the thrust washer 30 is attached to the inner ring 71 as in the bearing shown in FIG. That is, the circumferential groove 50 is formed in the outer diameter surface 78 on the large diameter side of the inner ring 71, and the flange 30 b of the thrust washer 30 is externally fitted to the large diameter portion of the inner ring 71, whereby the thrust washer is inserted into the circumferential groove 50. The hook part 32 of the 30 collar part 30b is hooked.

  Also in the bearings shown in FIGS. 8 and 9, the thrust washer 30 similar to the thrust washer 30 shown in FIG. 1 and the like is caught in the circumferential groove 50 like the circumferential groove 50 shown in FIG. The same effects as the embodiment shown in 1 etc. are exhibited.

  Thus, the bearing can be applied to various types, and this thrust washer is excellent in versatility. With the bearing of the present invention, it is possible to prevent the occurrence of stick-slip noise and wear of the inner ring end face and the like, and provide a bearing with excellent thrust washer incorporation.

  As described above, the embodiment of the present invention has been described. However, the present invention is not limited to the above embodiment, and various modifications are possible. For example, the tapered roller bearing shown in FIG. Whether it is the angular ball bearing shown or the tandem angular ball bearing shown in FIG. 9, the number of rolling elements (cone rollers, balls) can be increased or decreased arbitrarily. In the state shown in FIG. 2, the gap 59 is provided between the inner diameter surface 36 of the collar portion 30 b and the outer diameter surface 25 a of the large collar 25 of the inner ring 21. However, such a gap 59 is not provided. Also good.

21a Track surface 21b Axial end surface 21 Inner ring 22 Outer ring 22a Track surface 24 Cage 25a Outer diameter surface 30 Thrust washer 30a Disc-shaped main body 30b Hook 32 Hook-up part 37 Covered part 40 Notch (slit)
50 circumferential groove 51 bottom surface 55 clearance

Claims (14)

A thrust washer that is attached to the inner ring of the rolling bearing and prevents wear on one axial end face of the inner ring and the end face of the mating member facing the axial end face,
A disc-shaped main body facing one axial end surface of the inner ring, and a short cylindrical flange projecting on the outer peripheral edge of the disc-shaped main body and externally fitting one axial end of the inner ring, A thrust washer, characterized in that a hook portion is provided with a hook portion that protrudes toward the inner diameter side and hooks into a circumferential groove formed on the outer diameter surface of the inner ring, and the hook portion is divided by a notch portion.   3. The thrust washer according to claim 1, wherein three to eight hooks are arranged at a predetermined pitch along the circumferential direction.   The thrust washer according to claim 2, wherein the same number of hooks and notches are provided.   The escape portion that is not in contact with the catch portion when the catch portion is engaged with the circumferential groove is provided on the other axial end face side of the circumferential groove of the inner ring. 4. The thrust washer according to any one of 3 above.   The thrust washer according to any one of claims 1 to 4, wherein a notch bottom portion of the notch portion has a rounded shape.   The thrust washer according to any one of claims 1 to 5, wherein a circumferential notch width of the notch is set to 2 mm to 20 mm.   The thrust washer according to any one of claims 1 to 6, wherein the thickness of the disc-shaped main body and the flange portion is set to 0.3 mm to 0.8 mm.   The amount of protrusion from the inner diameter surface of the hook part of the hook part is set to plus or minus 0.2 mm with respect to the plate thickness of the disc-shaped main body and the hook part. Thrust washer as described in   The thrust washer according to any one of claims 1 to 8, wherein a clearance amount between the hook portion and a groove bottom of the circumferential groove is set to -0.3 mm to +0.5 mm.   The cover part which covers the inner ring | wheel outer-diameter surface of the anti-disk-shaped main-body side rather than the anti-disk-shaped main body side edge of the circumferential groove | channel was provided in the collar part. Thrust washer according to item.   The thrust washer according to any one of claims 1 to 10, wherein a nitride layer is provided on the surface.   The thrust washer according to any one of claims 1 to 11, wherein the material is SPCC or S60CM.   The thrust washer according to any one of claims 1 to 12, wherein the rolling bearing is one of a tapered roller bearing, a tandem angular ball bearing, and an angular ball bearing.   An inner ring, an outer ring, a plurality of rolling elements interposed between the inner ring and the outer ring, and a cage for holding the rolling elements, and a wearer having wear resistance is attached to an end of the inner ring. A bearing comprising the thrust washer according to any one of claims 1 to 13 as the washer.

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