JP2012167762A - Hermetic bearing device for vehicle - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a hermetic bearing device for a vehicle in which positioning members (rear lid or an oil cutter) can be easily attached to an inner wheel and the falling off of the positioning member from the inner wheel when press-fitting to the inner wheel shaft can be surely prevented.SOLUTION: In the hermetic bearing device for a vehicle having an outside raceway ring 4 and inside raceway rings 2 (2a, 2b) relatively rotatably oppositely arranged via a plurality of rollers 6a, 6b, a roller bearing A rotatably and pivotally supporting the wheel shaft S of various vehicles, an annular positioning members (rear lid F, the oil cutter P) for positioning the inside raceway rings in an axial direction, and hermetically sealing devices 70a, 70b sealing the inside from the outside to keep the inside in a hermetic condition, the positioning members are attached to the inside raceway rings via screw members 60 and integrated with the inside raceway rings.

Description

  The present invention relates to a bearing device used for, for example, an axle of a railway vehicle, and more specifically, a positioning member for preventing a positioning member (rear cover or oil drain) from being removed from the bearing when the bearing is pressed into the axle. It relates to the improvement of the mounting mechanism.

  FIG. 7 illustrates a configuration of a sealed bearing device for a railway vehicle (hereinafter also referred to as a bearing device). In the configuration example, the bearing device is externally fitted to the axle S so that the axle S is pivoted. Positioning member (rear side) for positioning the bearing (double row tapered roller bearing) A and the rotating wheel (inner ring as an example) 2 of the bearing A with respect to the axial direction (left-right direction in the figure). A lid F and a drainer P), and sealing devices 70a and 70b for sealing the inside of the bearing A from the outside to keep it sealed.

  Such a bearing A is connected to a wheel (not shown) and rotates together with the wheel (inner race ring (hereinafter referred to as inner ring)) 2 and a vehicle housing (not shown) and is always non-rotating. Can be rolled in a double row (for example, two rows) between a stationary wheel (outer raceway ring (hereinafter referred to as an outer ring)) 4 and a rotating wheel (inner ring) 2 and a stationary ring (outer ring) 4. Are provided with a plurality of rolling elements (rollers) 6a, 6b and a retainer 12 that rotatably holds the rolling elements (rollers) 6a, 6b one by one. In the configuration shown in FIG. 7, the inner ring 2 is composed of a first inner ring 2a and a second inner ring 2b. The first inner ring 2a is formed with a first raceway surface 8a and the second inner ring 2a. A second raceway surface 8b is formed on the inner ring 2b, and a double row (two rows) raceway surfaces 10a and 10b are formed on the outer ring 4 so as to face the first and second raceway surfaces 8a and 8b. Has been. An annular inner ring spacer 14 is interposed between the first inner ring 2a and the second inner ring 2b, and the end surface 2c of the first inner ring 2a and the end surface 14a of the inner ring spacer 14 are in contact with each other. The end surface 2d of the second inner ring 2b is in contact with the end surface 14b of the inner ring spacer 14.

As the positioning member, the rear lid F and the oil drain P are applied. The rear lid F and the oil drainer P are both substantially cylindrical and are fitted on the axle S. In this case, the end surface 2e of the first inner ring 2a and the end surface F1 of the rear lid F are in contact with each other, and the end surface 2f of the second inner ring 2b and the end surface P1 of the oil draining P are in contact with each other. In this way, the bearing A is axially moved by the inner ring 2 (2a, 2b) coming into contact with the rear lid F and the oil drain P, and the outer ring 4 is fixed to the vehicle housing (not shown). Are positioned along the left-right direction). The inner ring 2 (2a, 2b) and the outer ring 4 are made of bearing steel, and the rear cover F and the oil drain P are made of normalized carbon steel.
In the configuration shown in FIG. 7, the rear cover F has a stepped (two-step) cylindrical shape as an example, and its large-diameter inner peripheral surface F3 abuts on the outer peripheral surface large-diameter portion S2 of the axle S. The inner peripheral intermediate portion F5 connecting the large diameter inner peripheral surface F3 and the small diameter inner peripheral surface F4 contacts the outer peripheral surface stepped portion S1 of the axle S, and the small diameter inner peripheral surface F4 and the small diameter side A flange portion Ff provided continuously over the entire circumference on the inner circumferential surface F4 is externally fitted to the axle S so as to face the outer circumferential surface small diameter portion S3 of the axle S with a predetermined interval. In this case, the inner peripheral intermediate portion F5 of the rear lid F is formed in a convex curved surface shape that is continuous along the outer peripheral surface step portion S1 of the axle S.
In this state, the rear cover F has an end surface F1 on one end side (for example, the shaft end St side of the axle shaft S (left side in FIG. 7)) axially facing the end surface 2e of the inner ring 2 (first inner ring 2a) facing each other. (As an example, it is in contact from the right side in the figure).

On the other hand, the oil drain P is disposed on the entire circumference of the cylindrical main body Pm and the outer peripheral surface P2 on one end side of the main body Pm (for example, the shaft end St side of the axle shaft S (left side in FIG. 7)). It is comprised by the flange part Pf provided continuously over, and is externally fitted by the said axle shaft S so that the inner peripheral surface P3 of the main body Pm may contact | abut to the outer peripheral surface small diameter part S3 of the axle shaft S.
In this state, the oil drain P has an end surface P1 on one end side (as an example, on the right side in the figure) in an axial direction (in the same figure, the end surface 2f of the inner ring 2 (second inner ring 2b) facing the end face 2f. Is abutted from the left side, and an end surface P4 on the other end side (for example, the shaft end St side of the axle shaft S (left side in the figure)) abuts a fixing nut (not shown).

  Thus, in such a bearing device, the bearing A is such that the inner rings 2 (2a, 2b), the rear lid F and the oil drain P are opposite to each other in the axial direction (in FIG. 7, the left-right direction) facing each other. The outer ring 4 abuts and is fixed to a vehicle housing (not shown), thereby being positioned along the axial direction. Further, the inner ring 2 (2a, 2b), the rear cover F, and the oil drain P can be rotated together with the axle S in a state in which the end surfaces in the opposite axial directions (left and right in FIG. 7) are in contact with each other. Each is arranged. As an example, in the configuration shown in FIG. 7, the end surface F1 of the rear cover F and the end surface 2e of the first inner ring 2a are in contact with each other and are fitted and fixed to the axle S, and the rear cover F and the first cover are fixed. The inner ring 2a rotates with the axle S. Further, the end face P1 of the oil drain P and the end face 2f of the second inner ring 2b abut against each other and are fitted and fixed to the axle S, and the oil drain P and the second inner ring 2b rotate together with the axle S. ing.

  Further, the sealing devices 70a and 70b are configured such that the first inner ring 2a of the bearing A and the rear cover F are in contact with each other (end surfaces 2e and F1), and the second inner ring 2b of the bearing A and the oil drain P are in contact with each other. The bearing arrangement space 90 is sealed by covering the respective portions (end faces 2f, P1), and foreign matter (for example, water and dust) enters the bearing arrangement space 90 from the outside of the bearing device, and the bearing arrangement space. The leakage of lubricant (for example, lubricating oil or grease) from 90 to the outside of the bearing device is prevented. FIG. 8 shows, as an example, a configuration of a sealing device 70a that seals the bearing arrangement space 90 by covering a contact portion (end surfaces 2e, F1) between the first inner ring 2a and the rear lid F. Yes. In this sealing device 70a, as an example, a seal case 16a having a step-like cylindrical shape (for example, three steps) and a seal case 16a fitted in the seal case 16a, and the seal arrangement between the bearing arrangement space 90 and the seal device 70a are arranged. A partition plate 18a that separates the installation space (predetermined space in which the seal 30a is disposed) 92a in the axial direction (left-right direction in FIG. 8), and is fitted into the partition plate 18a, and the bearing installation space 90 is A seal 30a for sealing is provided.

  In this case, one end side (large-diameter annular portion 50) of the seal case 16a is fitted into the outer ring 4, and the other end side (small-diameter annular portion 54) extends in the direction of the rear lid F. The vicinity of the periphery is positioned so as to face the outer peripheral portion of the rear lid F with a predetermined interval (become a non-contact state). Further, between the large-diameter annular portion 50 and the small-diameter annular portion 54 of the seal case 16a, an intermediate-diameter annular portion that is smaller in diameter than the large-diameter annular portion 50 and larger in diameter than the small-diameter annular portion 54. 52 is provided. The large-diameter annular portion 50 and the medium-diameter annular portion 52 are connected by the large-diameter side connecting portion 56, and the medium-diameter annular portion 52 and the small-diameter annular portion 54 are connected by the small-diameter-side connecting portion 58. Thus, the seal case 16a is formed in a stepped cylindrical shape having three steps in cross section.

  The partition plate 18a is formed in an annular shape having a substantially L-shaped cross section, and its inner diameter is set slightly larger than the outer diameter of the small-diameter outer peripheral surface F2 of the rear lid F. At the same time, the outer diameter is set to be approximately the same as the inner diameter of the middle-diameter annular portion 52 of the seal case 16a. The partition plate 18a has an outer peripheral portion 18d along the medium-diameter annular portion 52 of the seal case 16a along the small-diameter annular portion 54 of the seal case 16a (outward direction of the bearing device (rightward in FIG. 8)). ) Is extended so as to be slightly smaller than the width dimension of the middle-diameter annular portion 52 (the dimension in the left-right direction in the figure). Thus, the partition plate 18a is fitted and fixed to the seal case 16a in a state where the outer peripheral portion 18d is in contact with the medium-diameter annular portion 52 of the seal case 16a. The lid F is opposed to the outer peripheral surface F2 on the small diameter side with a predetermined interval (gap 18s), and is positioned in a non-contact state with the rear lid F.

The seal 30a is configured by connecting a seal lip 34 made of various elastic materials (for example, a resin material such as rubber or plastic) to a part of an annular cored bar 32 having a substantially L-shaped cross section. ing. In this case, the inner diameter of the seal 30a is set to be approximately the same as the outer diameter of the outer peripheral surface F2 on the small diameter side of the rear lid F, and the outer diameter is approximately the same as the outer diameter of the partition plate 18a. And is fixed to the outer ring 4 via the partition plate 18a and the seal case 16a.
The seal lip 34 has two lips (a main lip 36 and a dust lip 38) that are in sliding contact with the outer peripheral surface F2 on the small diameter side of the rear lid F. The main lip 36 mainly prevents leakage of lubricant (for example, lubricating oil and grease) from the bearing arrangement space 90 to the outside of the apparatus, whereas the dust lip 38 mainly prevents the bearing arrangement space 90 from outside the apparatus. Foreign matter (for example, water or dust) is prevented from entering the main lip 36 toward the inside of the bearing device (left side in FIG. 8), and the dust lip 38 is located outside the bearing device (in FIG. 8). Are formed to be bifurcated from the inner peripheral edge of the cored bar 32 so as to extend toward the right). An annular core ring (garter spring) 40 is mounted on the outer peripheral side of the main lip 36 (the side opposite to the sliding contact side with the small-diameter outer peripheral surface F2 of the rear lid F). Is tightened in the direction of diameter reduction so as to be in close contact (close contact) with the outer peripheral surface F2 on the small diameter side of the rear lid F.

FIG. 8 shows, as an example, a configuration of a sealing device 70a that seals the bearing arrangement space 90 by covering the contact portions (end surfaces 2e, F1) between the first inner ring 2a and the rear lid F. However, the sealing device 70b that seals the bearing arrangement space 90 by covering the contact portion (end surfaces 2f, P1) between the second inner ring 2b and the oil drain P is configured in a similar manner (see FIG. 7). That is, the sealing device 70b is different in that the target member when the dimension is set (for example, the inner and outer diameters of the seal case 16b, the partition plate 18b, and the seal 30b) is the oil drainage P, but has other shapes and structures. Are configured in the same manner as the seal case 16a, the partition plate 18a, and the seal 30a in the sealing device 70a of the contact portion (end surfaces 2e, F1) between the first inner ring 2a and the rear lid F shown in FIG.
In the sealing device 70b, the seal case 16b has one end side (large-diameter annular portion 50) in the axial direction (left-right direction in FIG. 7) fitted into the outer ring 4 and the other end side (small-diameter annular portion 54). It extends in the direction of oil drainage P, and is positioned so that the vicinity of the inner peripheral edge on the other end side faces the flange portion Pf of the oil drainage P with a predetermined interval (becomes a non-contact state). Further, the seal lip 34 (main lip 36 and dust lip 38) of the seal 30b is in sliding contact with the outer peripheral surface P2 of the body Pm of the oil drain P (see FIG. 7).

By the way, the rear lid F and the oil drain P, which are positioning members, are attached to the bearing A by tightening in the diameter reducing direction by the garter spring 40 attached to the main lip 36 of the seals 30a, 30b. And integrated.
However, with the recent increase in the speed of railway vehicles, for example, in order to suppress heat generation during high-speed rotation of the bearing A while maintaining the sealability of the seals 30a and 30b, the seal lip 34 (for example, the main lip 36) and a sealing structure that makes the small-diameter outer peripheral surface F2 of the rear lid F lightly contact or non-contact may be employed. In this case, when the bearing A is press-fitted into the axle shaft S, the inner ring 2 and the positioning member (specifically, the first inner ring 2a and the rear cover F or the second inner ring 2b and the oil are simply tightened by the garter spring 40). The inner ring 2 (2a, 2b) and the positioning member (rear cover F and oil drain P) are separated from each other, and the rear cover F and the oil drain P are separated from the inner ring 2 (2a). , 2b) may come off (drop off).

  For this reason, various measures have been conventionally taken to prevent the positioning members (rear cover F and oil drain P) from falling off from the inner ring 2 (2a, 2b) when the bearing A is pressed into the axle S. Has been. For example, in Patent Document 1, the inner ring and the rear lid are provided with a convex portion on one side and a concave portion on the other side, and these are engaged with each other by clearance fitting to prevent the rear lid from falling off the inner ring. A configuration of a sealed bearing device for a vehicle is disclosed.

JP 2008-267431 A

  However, in the sealed bearing device for a vehicle disclosed in Patent Document 1, the concave and convex portions provided on the inner ring and the rear lid are merely engaged with each other by clearance fitting, and the bearing A is pressed into the axle S. Depending on the conditions such as the load or the weight of the inner ring and the rear lid, the once-engaged irregularities may come off during press-fitting, causing the inner ring and the rear lid to be separated. The prevention mechanism is not always sufficient.

  The present invention has been made to solve such a problem, and the purpose thereof is to enable a positioning member (rear cover or oil drain) to be easily attached to an inner ring and to press-fit a bearing into an axle. An object of the present invention is to provide a sealed bearing device for a vehicle that can reliably prevent a positioning member (rear cover or oil drain) from dropping from an inner ring at the time.

  In order to achieve such an object, a sealed bearing device for a vehicle according to the present invention includes an outer raceway and an inner raceway that are opposed to each other so as to be relatively rotatable via a plurality of rolling elements. A rolling bearing for pivotally supporting a vehicle axle; an annular positioning member for positioning the inner race in the axial direction; and a sealing device for sealing the inside from the outside to keep it sealed. It has. In such a sealed bearing device for a vehicle, the positioning member is attached to the inner raceway through a screw member, and is integrated with the inner raceway.

  In this case, the screw member is formed in a substantially cylindrical shape, and one end side in the extending direction of the cylinder is fixed to the inner peripheral portion of the inner raceway, and is exposed from the inner raceway in the fixed state. A spiral screw groove is formed on the outer peripheral portion on the other end side in the extending direction, and the positioning member has a spiral screw groove that can be screwed into the screw groove formed on the screw member on the inner peripheral portion. And what is necessary is just to fix to the said screw member by screwing these screw grooves.

  Alternatively, the screw member extends in a cylindrical shape along the vicinity of the outer peripheral edge of the positioning member of the inner race ring, and is fixed to the vicinity of the outer peripheral edge of the inner race ring. An annular flat plate portion extending in a reduced diameter direction along an end surface on the mounting side of the inner race ring continuously to the extending end of the fixed portion, and the mounting continuously to an inner peripheral edge of the flat plate portion. And having a tip portion extending in a cylindrical shape toward the side, forming a helical screw groove on the outer periphery of the tip portion, and the positioning member being formed at the tip portion of the screw member. Alternatively, a helical screw groove that can be screwed with the screw groove is formed in the inner peripheral portion, and the screw groove may be screwed to be fixed to the tip portion of the screw member.

  In any case, the positioning member can be either one or both of the rear lid and the oil drain.

  According to the sealed bearing device for a vehicle according to the present invention, the positioning member (rear cover or oil drain) can be easily attached to the inner ring, and the positioning member (rear side) from the inner ring when the bearing is press-fitted into the axle. It is possible to reliably prevent the lid and oil drain) from falling off. As a result, such press-fitting work can be performed very smoothly and with high accuracy.

It is sectional drawing which shows the whole structure of the sealed bearing apparatus for wheel support which concerns on 1st Embodiment of this invention. It is a figure showing the state where the sealed bearing device for wheel support concerning a 1st embodiment of the present invention was press-fitted into an axle. In FIG. 2, it is a figure which expands and shows the state in which the rear cover is attached to the inner ring via a cylindrical screw member. The figure which expands and shows the state by which the rear cover is attached to the inner ring | wheel via the staircase cylindrical screw member, when the sealed bearing apparatus for wheel support which concerns on 2nd Embodiment of this invention is press-fitted in an axle shaft. It is. It is a figure which shows the state in which the rear cover and the oil drain are both attached to the inner ring via a cylindrical screw member. It is a figure which shows the state in which the back cover and the oil drain are both attached to the inner ring via a stepped cylindrical screw member. It is a figure which shows the state which made the conventional wheel support sealed bearing apparatus press-fit into an axle shaft. In FIG. 7, it is a figure which expands and shows the state in which the rear cover is attached with respect to the inner ring.

  Hereinafter, a sealed bearing device for a vehicle (hereinafter also referred to as a bearing device) according to an embodiment of the present invention will be described with reference to the accompanying drawings. The bearing device of the present invention can be applied as, for example, a bearing device for supporting the axles of various vehicles such as railways and automobiles. Here, the bearing device is used to support the axles of a rail vehicle. As an example, assume that Further, the present invention provides a positioning member for preventing a positioning member (for example, a rear cover or a drain) from coming off from a bearing portion (for example, an inner race) of the bearing device when the bearing device is press-fitted into an axle. This relates to the improvement of the mounting mechanism, and the basic configuration of the bearing device can be assumed to be the same as that of the above-described railway vehicle bearing device (FIGS. 7 and 8). Therefore, here, the basic configuration of the bearing device is assumed to be the same as that of the bearing device (FIGS. 7 and 8) as an example, and the following description is based on the member configuration. In this case, the same or similar components as those of the above-described bearing device (FIGS. 7 and 8) are denoted by the same reference numerals in the drawings, and the description thereof is omitted or simplified. Hereinafter, the bearing device of the present invention will be described. The positioning member attaching mechanism peculiar to the above will be described in detail.

1 to 3 show the configuration of a sealed bearing device for a vehicle according to a first embodiment of the present invention. Such a bearing device includes an outer race ring 4 and an inner race ring 2 (first inner ring 2a and second inner race ring 2) that are opposed to each other so as to be relatively rotatable via a plurality of rolling elements (for example, tapered rollers) 6a and 6b. Rolling bearings (double-row tapered roller bearings (hereinafter simply referred to as bearings)) A, and the inner race rings 2 (2a, 2b). ) In the axial direction, and sealing devices 70a and 70b (sealing cases 70a and 70b for sealing the interior of the bearing A from the outside to keep it sealed. 16a, 16b, partition plates 18a, 18b, and seals 30a, 30b).
In the configuration shown in FIG. 1 to FIG. 3, the inner race ring (hereinafter referred to as the inner ring) 2 has a divided structure of the first inner ring 2a and the second inner ring 2b. Similarly to the outer ring 4, an integral structure having double-row raceway surfaces 8 a and 8 b may be used. It is also possible to assume that the outer ring 4 has a divided structure with two track bodies.
In addition, an inner ring spacer 14 is interposed between the first inner ring 2a and the second inner ring 2b, but without the inner ring spacer 14, the end surface 2c of the first inner ring 2a and the second inner ring 2a The end surface 2d of the second inner ring 2b may be in direct contact with the end surface 2d.
In addition, it is assumed that tapered rollers 6a and 6b are incorporated as rolling elements, but instead of such tapered rollers, cylindrical rollers, spherical rollers (drum type rollers), hollow rollers, or balls are incorporated. Can also be envisaged.

In the present embodiment, the positioning member is attached to the inner ring 2 via a screw member and integrated with the inner ring 2. As an example, in FIGS. 1 to 3, a configuration in which the rear lid F is attached to the inner ring 2 via the screw member 60 and integrated with the inner ring 2 is shown as an example.
In this case, the screw member 60 has a substantially cylindrical shape, and one end side in the extending direction of the cylinder (the left end side in FIGS. 1 to 3) is the inner ring 2 (specifically, the first inner ring 2a). Fixed to the periphery. The first inner ring 2a has a stepped portion (hereinafter referred to as a screw member fixing portion) in which the vicinity of the inner peripheral edge of the attachment side (right side in FIGS. 1 to 3) of the rear lid F is enlarged over the entire circumference. ) 20a is formed. The diameter dimension of the screw member fixing portion 20a is set to be substantially the same as the outer diameter dimension of the screw member 60, and the width dimension with respect to the axial direction (left and right direction in FIGS. 1 to 3) is the extension of the screw member 60. It is set smaller than the dimensions. The outer diameter of the screw member 60 is set to be substantially the same as the inner diameter of the flange portion Ff of the rear lid F, and the inner diameter of the screw member 60 is the side where the screw member fixing portion 20a of the first inner ring 2a is formed. Is set slightly larger than the inner diameter in the vicinity of the inner peripheral edge (the step height of the step portion 22a of the screw member fixing portion 20a).

  By forming such a screw member fixing portion 20a with respect to the first inner ring 2a, the screw member 60 is fitted (internally fitted) into the screw member fixing portion 20a by press-fitting. It can be fixed to the first inner ring 2a. When press-fitting into the screw member fixing portion 20a, first, the screw member 60 is first attached to the attachment side (the right side in FIGS. 1 to 3) of the rear cover F of the first inner ring 2a. Positioned concentrically with 2a, the screw member 60 is press-fitted into the screw member fixing portion 20a from this state. Then, the screw member 60 is pressed and inserted until an end portion (hereinafter referred to as a press-fitting side end portion) 62 in the extending direction of the screw member 60 comes into contact with the stepped portion 22a of the screw member fixing portion 20a. The vicinity (hereinafter, referred to as a screw member press-fit portion 64) of the press-fit side end portion 62 of the member 60 can be fitted (internally fitted) to the screw member fixing portion 20a.

  Note that the axial width dimension of the screw member fixing portion 20a is determined when the screw member 60 is press-fitted into the screw member fixing portion 20a to be fitted therein (further, as described later, the rear lid F is attached to the screw member 60). (When fixed) is set according to the extension dimension of the screw member 60 so that the screw member 60 can be fixed to the first inner ring 2a in a stable state. do it. In the configuration shown in FIGS. 1 to 3, as an example, the axial width dimension of the screw member fixing portion 20 a is set to about one third of the extension dimension of the screw member 60. Further, the fixing method of the screw member 60 to the first inner ring 2a (screw member fixing portion 20a) is not limited to press-fitting (internal fitting), but instead of or in addition, for example, bonding with an adhesive, It is also possible to assume various methods such as welding or screwing (including screws and rivets). In addition, the screw member 60 may be made of metal (for example, iron) or resin. However, the screw member 60 is not limited to this, and any material may be used depending on the material of the inner ring 2 (first inner ring 2a). Can be configured.

  The screw member 60 has a spiral screw groove 68 on the outer peripheral portion on the other end side in the extending direction (right end side in FIGS. 1 to 3) exposed from the first inner ring 2 a in the fixed state. Is formed. That is, the screw member 60 is a member other than the screw member press-fitting portion 64 exposed from the screw member fixing portion 20a in a state in which the screw member press-fitting portion 64 is fitted into the screw member fixing portion 20a of the first inner ring 2a. This is a structure in which a spiral screw groove 68 is formed on the outer peripheral portion of this portion (hereinafter referred to as a screw member exposed portion 66). As a result, even if the screw member press-fitting portion 64 is press-fitted (internally fitted) into the screw member fixing portion 20a, the screw groove 68 formed in the screw member exposed portion 66 is formed in the rear of the first inner ring 2a. The cover F can be exposed to the attachment side (the right side in FIGS. 1 to 3).

  On the other hand, the rear lid F has a spiral thread groove Fs that can be screwed into the thread groove 68 formed in the screw member 60 on the inner peripheral portion. As an example, FIGS. 1 to 3 show an example of the configuration of the rear lid F in which the thread groove Fs is formed in the inner peripheral portion of the flange portion Ff of the rear lid F. In this case, a series of screw grooves Fs are formed in a spiral shape over the entire inner peripheral portion of the flange portion Ff. Thus, by screwing the screw groove Fs with the screw groove 68 of the screw member 60, the entire flange portion Ff is fastened to the screw member exposed portion 66, and the rear lid F can be securely fixed to the screw member 60. it can. That is, the rear lid F can be easily attached to the first inner ring 2a via the screw member 60, and the rear lid F and the first inner ring 2a can be integrated. The thread height Fs of the back cover F and the thread groove 68 of the screw member 60 can be arbitrarily set as long as the height of the crest, the depth of the trough, the pitch, and the like can be screwed together. Absent.

When fixing the rear cover F to the screw member 60, first, the rear cover F is placed on the screw member exposed portion 66 side (right side in FIGS. 1 to 3) of the screw member 60 with the screw member exposed portion 66. The screw groove Fs of the flange portion Ff is screwed with the screw groove 68 of the screw member exposed portion 66 from the concentric position. Then, both the thread grooves Fs and 68 are screwed together until the end face F1 of the rear lid F (flange portion Ff) comes into contact with the end surface 2e of the first inner ring 2a, so that the rear lid F is moved over the entire flange portion Ff. The screw member 60 can be securely fixed.
At that time, while rotating the rear lid F in the circumferential direction with respect to the screw member 60 (screw member exposed portion 66), the axial direction (FIGS. 1 to 3) until the end face F1 contacts the end face 2e of the first inner ring 2a. In FIG. 3, the left side is gradually moved (to the left), so that it is possible to effectively prevent the dust lip 38 in sliding contact with the small-diameter outer peripheral surface F2 of the rear lid F from being inverted. That is, it is possible to prevent a reduction in sealing performance (for example, an effect of suppressing foreign matter intrusion from the outside) due to the dust lip 38 being inverted when the rear lid F is attached to the first inner ring 2a. It is also possible to improve the durability of the seal 30a.

  As described above, according to the bearing device according to the present embodiment, the positioning member (rear cover F) can be easily attached to the inner ring 2 (first inner ring 2a), and to the axle S of the bearing A. It is possible to reliably prevent the positioning member (rear cover F) from falling off from the inner ring 2 (first inner ring 2a) during the press-fitting. As a result, such press-fitting work can be performed very smoothly and with high accuracy.

  In the above-described embodiment (FIGS. 1 to 3), the screw member 60 has a substantially cylindrical shape and is press-fitted to the screw member fixing portion 20a of the inner ring 2 (first inner ring 2a) ( The screw member 60 is fixed to the first inner ring 2a by being internally fitted), but the configuration of the screw member 60 is not limited to this. For example, like the screw member 80 according to the second embodiment of the present invention shown in FIG. 4, the screw member 80 may be externally fixed to the first inner ring 2 a as shown in FIG. From FIG. 3), the same operational effects can be achieved. The second embodiment (FIG. 4) of the present invention will be described below. In that case, since the configuration of the bearing device other than the screw member 80 and the first inner ring 2a is the same as that of the first embodiment (FIGS. 1 to 3) described above, the configuration peculiar to the second embodiment will be described below. The description of (the screw member 80 and the first inner ring 2a) will be stopped.

  In the present embodiment, as shown in FIG. 4, the screw member 80 is in the vicinity of the outer peripheral edge on the attachment side (right side in FIG. 4) of the rear lid F of the inner ring 2 (specifically, the first inner ring 2a). A fixing portion 82 that extends in a cylindrical shape along the (large-diameter side flange) and is fixed in the vicinity of the outer peripheral edge of the first inner ring 2a, and a first continuous with the extending end of the fixing portion 82. An annular flat plate portion 84 extending in the diameter reducing direction along the attachment-side end surface 2e of the inner ring 2a and a cylindrical shape extending toward the attachment side continuously to the inner peripheral edge of the flat plate portion 84. A tip portion 86 is provided. In this case, the fixed portion 82 on the large diameter side and the distal end portion 86 on the small diameter side are both continuous with the flat plate portion 84 at a substantially right angle, and the screw member 80 has a stepped cylindrical shape with two steps in cross section. Eggplant. The fixing portion 82 of the screw member 80 has an inner diameter dimension set to be substantially the same as an outer diameter dimension in the vicinity of the outer peripheral edge (large diameter side flange portion) of the first inner ring 2a on the attachment side of the rear lid F. The outer diameter of the portion 86 is set to be substantially the same as the inner diameter of the flange portion Ff of the rear lid F, and the inner diameter is in the vicinity of the inner peripheral edge of the first inner ring 2a on the attachment side of the rear lid F. The inner diameter is set to be slightly larger than the inner diameter. Further, the flat plate portion 84 of the screw member 80 is extended in the diameter-reducing direction with a dimension (wall thickness of the large-diameter side flange) substantially corresponding to the outer diameter side to the inner diameter side of the end surface 2e of the first inner ring 2a. ing.

  The first inner ring 2a has one groove portion (hereinafter referred to as a screw member engagement groove) formed by reducing the diameter of the vicinity of the outer peripheral edge of the rear lid F on the attachment side (right side in FIG. 4). ) 24a is formed. On the other hand, the fixed portion 82 of the screw member 80 is formed with a single protrusion 83 whose inner peripheral portion is reduced in diameter over the entire circumference and can be engaged with the screw member engaging groove 24a. ing. The cross-sectional shape and depth (diameter dimension) of these screw member engaging grooves 24a and the cross-sectional shape and height (diameter dimension) of the protrusion 83 are set so that they can be engaged with each other. Further, the positions where these screw member engaging grooves 24a and protrusions 83 are formed in the axial direction (left and right direction in FIG. 4) are fitted (externally engaged) by press-fitting the screw member 80 into the first inner ring 2a as will be described later. When the flat plate portion 84 of the screw member 80 is in contact with the end surface 2e of the first inner ring 2a, the protrusion 83 is mutually engaged with the screw member engaging groove 24a. You only have to set it. FIG. 4 shows an example in which one protrusion 83 and one screw member engaging groove 24a are formed, but the screw member 80 is press-fitted into the first inner ring 2a as will be described later. A plurality of each may be formed as long as they can be engaged with each other when they are externally fitted.

When the screw member 80 is press-fitted and fitted to the vicinity of the outer peripheral edge of the first inner ring 2a, first, the screw member 80 is placed on the attachment side (right side in FIG. 4) of the rear cover F of the first inner ring 2a. Positioned concentrically with the first inner ring 2a, the fixing portion 82 of the screw member 80 is press-fitted into the vicinity of the outer peripheral edge of the first inner ring 2a. Then, when the flat plate portion 84 of the screw member 80 is pressed and fitted until it contacts the end surface 2e of the first inner ring 2a, the protrusion 83 of the fixing portion 82 becomes the screw member engaging groove 24a of the first inner ring 2a. Is engaged. As a result, the fixing portion 82 is locked to the screw member engaging groove 24a via the protrusion 83, and the screw member 80 is reliably fitted (externally fitted) to the vicinity of the outer peripheral edge of the first inner ring 2a. In addition, the screw member 80 can be effectively prevented from falling off the first inner ring 2a.
The method of fixing the screw member 80 to the first inner ring 2a is not limited to press-fitting (outer fitting), but instead of or in addition, for example, bonding with an adhesive, welding, or screw (screw or As in the case of the first embodiment (FIGS. 1 to 3) described above, it is possible to envisage adopting various methods such as fastening (including rivets). Further, the screw member 80 may be made of metal (for example, iron) or resin, but is not limited thereto, and is made of any material according to the material of the inner ring 2 (first inner ring 2a). The configuration is also possible as in the case of the first embodiment (FIGS. 1 to 3) described above.

In the screw member 80, a spiral thread groove 88 is formed on the outer peripheral portion of the distal end portion 86. That is, even if the screw member 80 is in a state in which the fixing portion 82 is press-fitted (externally fitted) to the vicinity of the outer peripheral edge of the first inner ring 2a, the screw groove 88 formed in the distal end portion 86 is formed in the first groove 86. The inner ring 2a is exposed to the attachment side (the right side in FIG. 4) of the rear lid F.
On the other hand, the rear lid F has a helical thread groove Fs that can be screwed into the thread groove 88 formed in the screw member 80 on the inner peripheral portion. As an example, FIG. 4 shows an example of the configuration of the rear lid F in which the thread groove Fs is formed in the inner peripheral portion of the flange portion Ff of the rear lid F. In this case, a series of screw grooves Fs are formed in a spiral shape over the entire inner peripheral portion of the flange portion Ff. Thereby, by screwing the screw groove Fs with the screw groove 88 of the screw member 80, the entire flange portion Ff is fastened to the tip end portion 86, and the rear lid F can be reliably fixed to the screw member 80. That is, the rear cover F can be easily attached to the first inner ring 2a via the screw member 80, and the rear cover F and the first inner ring 2a can be integrated. This is the same as in the case of FIGS. In addition, as long as the screw groove Fs of the back cover F and the screw groove 88 of the screw member 80 can be screwed together, the height of the peak, the depth of the valley, the pitch, etc. may be set arbitrarily. Absent.

  When the rear lid F is fixed to the distal end portion 86 of the screw member 80, first, the rear lid F is concentrically with the distal end portion 86 on the distal end portion 86 side (right side in FIG. 4) of the screw member 80. The screw groove Fs of the flange portion Ff is screwed with the screw groove 88 of the distal end portion 86 from that state. Then, both the thread grooves Fs and 88 are screwed together until the end face F1 of the rear lid F (flange portion Ff) comes into contact with the flat plate portion 84 of the screw member 80, so that the rear lid F is reliably secured to the entire flange portion Ff. It can be fixed to the screw member 80. At that time, while rotating the rear lid F in the circumferential direction with respect to the screw member 80 (tip portion 86), it gradually moves in the axial direction (leftward in FIG. 4) until the end surface F1 contacts the flat plate portion 84. Therefore, it is possible to effectively prevent the dust lip 38 in sliding contact with the small-diameter outer peripheral surface F2 of the rear lid F from being reversed, as in the case of the first embodiment (FIGS. 1 to 3) described above. .

  Here, in the first embodiment (FIGS. 1 to 3) and the second embodiment (FIG. 4) described above, the rear cover F, which is one of the positioning members, is screwed to the first inner ring 2a. It is assumed that the first inner ring 2a and the first inner ring 2a are attached to each other, and similarly, the oil drain P as a positioning member is screwed to the inner ring 2 (second inner ring 2b). It is also possible to attach via the members 60 and 80 and to integrate with the second inner ring 2b. As a result, the oil drain P can be easily attached to the second inner ring 2b, and the oil drain P can be reliably prevented from falling off from the second inner ring 2b when the bearing A is pressed into the axle S. can do. As a result, such press-fitting work can be performed very smoothly and with high accuracy.

  In this way, when the oil drain P is attached to the second inner ring 2b via the screw members 60 and 80 and integrated with the second inner ring 2b, the above-described first embodiment (FIG. 1 to FIG. Similarly to the case of 3), a portion corresponding to the screw member fixing portion 20a is formed in the second inner ring 2b, and the screw member 60 (screw member press-fit portion 64) is internally fitted by press-fitting. The thread groove 68 and the thread groove Ps formed on the inner peripheral surface P3 of the oil drain P (main body Pm) may be screwed together (see FIG. 5). Alternatively, as in the case of the second embodiment (FIG. 4) described above, a groove corresponding to the screw member engaging groove 24a is formed in the second inner ring 2b, and the screw member 80 (fixed portion 82) is attached to the second inner ring 2b. While engaging the outer periphery of the inner ring 2b by press-fitting and engaging the protrusion 83 with the groove portion of the second inner ring 2b, the thread groove 88 of the screw member 80 and the oil drain P (main body Pm) What is necessary is just to screw together with the thread groove Ps formed in the internal peripheral surface P3 (refer FIG. 6).

In FIG. 5, the rear lid F is attached to the first inner ring 2 a via the screw member 60 (fixed by internal fitting), integrated with the first inner ring 2 a, and the oil drain P is connected to the second inner ring 2. A configuration of a bearing device attached to 2b via a similar screw member 60 and integrated with the second inner ring 2b is shown as an example. In FIG. 6, the rear lid F is attached to the first inner ring 2 a via a screw member 80 (fixed by external fitting), integrated with the first inner ring 2 a, and the oil drain P is second A configuration of a bearing device that is attached to the inner ring 2b via a similar screw member 80 (fixed by external fitting) and integrated with the second inner ring 2b is shown as an example.
In any configuration, the oil drainage P (main body Pm) is provided with a screw member 60, the vicinity of the peripheral edge of the inner peripheral surface P3 on the side attached to the second inner ring 2b (right side in FIGS. 5 and 6). Corresponding to the wall thickness (inside / outside diameter difference) of 80 (screw member exposed portion 66 or tip portion 86), a stepped portion P5 is formed which is enlarged over the entire circumference. The step portion P5 is set to have a diameter dimension substantially the same as the outer diameter dimension of the screw members 60, 80 (the screw member exposed portion 66 or the tip end portion 86), and the axial direction (in FIGS. The width dimension with respect to (direction) is set to be larger than the extension dimension of the screw member exposed portion 66 or the distal end portion 86, and a thread groove Ps is formed in the inner peripheral portion thereof.

  5 and 6, both the rear lid F and the oil drain P are attached to the inner ring 2 (first inner ring 2a and second inner ring 2b) by the same mounting mechanism (screw member 60 or screw member 80). Although the structure of the bearing device integrated with the inner ring 2 (2a, 2b) is shown, the inner ring 2 is connected to the rear lid F and the oil drain P via different mounting mechanisms (screw member 60 and screw member 80). It is also possible to attach to (the first inner ring 2a and the second inner ring 2b) and integrate with the inner ring 2 (2a, 2b). For example, the rear lid F is attached to the first inner ring 2a via the screw member 60, integrated with the first inner ring 2a, and the oil drain P is attached to the second inner ring 2b via the screw member 80, It may be integrated with the second inner ring 2b. Alternatively, conversely, the rear lid F is attached to the first inner ring 2 a via the screw member 80, integrated with the first inner ring 2 a, and the oil drain P is connected to the second inner ring 2 a via the screw member 60. It may be attached to the inner ring 2b and integrated with the second inner ring 2b.

2 Inner race ring (inner ring)
2a First inner ring 2b Second inner ring 4 Outer race ring (outer ring)
6a, 6b Rolling elements (cone rollers)
60, 80 Screw members 70a, 70b Sealing device A Rolling bearing F Rear cover P Oil drain S Axle

Claims (4)

A rolling bearing having an outer race ring and an inner race ring that are opposed to each other via a plurality of rolling elements and rotatably supports the axles of various vehicles, and the inner race ring as a shaft. A sealed bearing device for a vehicle including an annular positioning member for positioning in a direction and a sealing device for sealing the inside from the outside to keep it sealed.
The said positioning member is attached to the said inner raceway via the screw member, and is integrated with the said inner raceway, The sealed bearing apparatus for vehicles characterized by the above-mentioned. The screw member has a substantially cylindrical shape, and one end side in the extending direction of the cylinder is fixed to the inner peripheral portion of the inner race, and the extension exposed from the inner race in the fixed state. A spiral thread groove is formed on the outer peripheral portion on the other end side in the outgoing direction,
The positioning member is formed with a spiral screw groove that can be screwed with a screw groove formed in the screw member, and is fixed to the screw member by screwing these screw grooves. The sealed bearing device for a vehicle according to claim 1, wherein: The screw member extends in a cylindrical shape along the vicinity of the outer peripheral edge of the inner race ring on the attachment side of the positioning member, and is fixed to the vicinity of the outer peripheral edge of the inner race ring, and the fixing An annular flat plate portion extending in the diameter-reducing direction along the end surface on the attachment side of the inner race, and an inner peripheral edge of the flat plate portion toward the attachment side. Having a tip extending in a cylindrical shape toward the outer periphery, and a spiral thread groove is formed on the outer periphery of the tip.
In the positioning member, a spiral thread groove that can be screwed with a thread groove formed at a tip portion of the screw member is formed in an inner peripheral part, and by screwing these screw grooves, The sealed bearing device for a vehicle according to claim 1, wherein the sealed bearing device is for a vehicle.   4. The vehicle bearing device according to claim 1, wherein the positioning member is one or both of a rear lid and an oil drain.

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