JP5104516B2 - Bearing sealing device mounting structure - Google Patents

Description

  The present invention relates to a bearing sealing device mounting structure for keeping the inside of various bearings (for example, a bearing device such as a hub unit bearing (wheel support bearing unit) for supporting automobile wheels) in a sealed state. In particular, the present invention relates to an improvement in the deformation preventing structure of the sealing device attached to the wheel support bearing unit.

  Conventionally, various sealing devices are attached to the bearing device in order to shield the inside of the bearing from the outside and keep it in a sealed state (airtight state and liquid tight state), and by attaching the sealing device, Prevents foreign matter (e.g., muddy water, dust, etc.) from entering the bearing device from the outside, and prevents lubricant (e.g., grease, lubricating oil, etc.) enclosed inside from leaking to the outside. It is preventing.

  Such a sealing device can be roughly classified into a contact type and a non-contact type. For example, as the contact type, an annular core formed by pressing a steel plate or the like so that the cross section is L-shaped. There is a seal that has a structure in which various elastic materials (for example, resin materials such as rubber and plastic) are connected to a part of gold, and as a non-contact type, it is pressed from a metal plate (steel plate) such as a stainless steel plate or an iron plate. There is a shield molded by processing. Furthermore, a contact-type sealing device (so-called pack seal) having a package structure obtained by combining the contact-type seal and the non-contact-type shield (so-called slinger) so that the cross-sectional shape is substantially box-shaped (rectangular) is also known. (FIG. 3A).

In general, the contact type has higher sealing performance than the non-contact type, and depending on the level of hermeticity (air tightness and liquid tightness) required according to the use conditions and purpose of the bearing device, these Different sealing devices are used.
As an example, the pack seal not only has the feature that its cross-sectional area is small and it is not necessary to secure a large installation space, but also has an excellent feature that its sealing performance is very high, so it has a strict sealing performance ( For example, a bearing device that requires a high level of muddy water intrusion prevention effect, for example, a sealing device for a hub unit bearing (hereinafter referred to as a bearing unit) A for supporting a vehicle wheel as shown in FIG. Widely used (see Patent Document 1).

  FIG. 3A shows an example of the configuration of the pack seal 2, and the pack seal 2 includes a slinger 22 and a core metal (hereinafter referred to as a seal core metal) that are arranged to face each other at a predetermined interval. 24) and a seal 26 interposed therebetween (see the dotted circle in the figure). In this case, the slinger 22 and the seal core 24 are both formed in an annular shape having a substantially L-shaped cross section, and the seal 26 is connected to one of the slinger 22 or the seal core 24, A plurality of lips 26l that are in sliding contact with the other are provided.

  When the pack seal 2 having such a configuration is assembled to the bearing unit A as shown in FIG. 3A, the slinger 22 is fixed to the rotating wheel 10 (specifically, the inner ring component 16) ( Specifically, the seal cored bar 24 is fixed (specifically fitted) to the stationary ring 12 and is always rotated while being rotated together with the rotating wheel 10 (inner ring component 16). It remains stationary. In the configuration shown in FIG. 3A, the seal 26 is stationary with the lip 26l slidingly contacted with the rotating slinger 22.

By the way, the slinger 22 and the seal metal core 24 of the pack seal 2 are usually formed by pressing a thin steel plate or the like in consideration of ease of processing and cost, and the rotating wheel 10 (inner ring configuration of the bearing unit A). The body 16) and the stationary ring 12 are fitted and positioned and fixed.
For example, in the slinger 22 of the pack seal 2 as shown in FIG. 3A, the inner peripheral surface of the cylindrical fixing portion 22a (the lower surface in the dotted circle in the figure) is the rotating wheel 10 of the bearing unit A. With respect to the rotating wheel 10 (inner ring component 16) so as to come into contact with the fitting surface (groove shoulder portion of the raceway surface 10i) 10s (the same figure (b), (c)) of the (inner ring component 16). Are mated.

  As described above, when the slinger 22 is fitted to the rotating wheel 10 (inner ring structure 16), the slinger 22 is subjected to hoop stress due to the fitting, but as described above, the thickness is made substantially uniform by pressing or the like. In the case of the molded slinger 22, generally the rigidity of the slinger 22 with respect to the hoop stress is higher in the disc portion 22b than in the fixed portion 22a. For this reason, when the slinger 22 is fitted, for example, when the disk portion 22b is deformed so as to tilt forward with respect to the fitting direction of the slinger 22 (FIG. 3B), or the fixing portion 22a is There is a case where the tip portion is deformed in the diameter increasing direction so as to be lifted ((c) in the figure).

For example, as shown in FIG. 3B, when the slinger 22 is deformed by tilting the disc portion 22b forward, the sliding contact state between the slinger 22 and the lip 261 of the seal 26 (so-called squeezing margin of the lip 261) is achieved. (Hereinafter simply referred to as “squeeze allowance”) will change, specifically, the allowance will increase.
When the interference is increased, the slinger 22 and the seal 26 (lip 26l) are excessively slidably contacted to generate heat due to friction, leading to early deterioration of the slinger 22 and the seal 26, and the sealing performance of the pack seal 2 (for example, There is a risk of reducing the muddy water infiltration prevention effect.
In addition, as shown in FIG. 3B, when the encoder 28 which is the detection target of the sensor (not shown) is provided on the disc portion 22b of the slinger 22, the disc portion 22b is inclined forward. If it is deformed, the air gap between the encoder 28 and the sensor changes, so that the measurement accuracy of the rotation state (for example, the rotation speed, the rotation direction, or the rotation angle) of the rotating wheel 10 (inner ring structure 16) is lowered. There is a fear.

  On the other hand, as shown in FIG. 3 (c), when the slinger 22 is deformed by lifting the tip portion of the fixing portion 22a, the slinger 22 is a continuous portion of the fixing portion 22a and the disc portion 22b (hereinafter referred to as “the slinger 22”). , Called a bent part) at the position where the chamfer is stopped (R stop), and abuts on the fitting surface 10s of the rotating wheel 10 (inner ring structure 16). That is, the slinger 22 and the fitting surface 10s of the rotating wheel 10 (inner ring structure 16) are brought into a line contact state, and the contact area is reduced. Therefore, the fitting portion between the slinger 22 and the fitting surface 10s ( Water intrusion from the line contact portion) is likely to occur, and the sealing performance of the pack seal 2 (for example, muddy water intrusion prevention effect) may be reduced.

Therefore, in order to eliminate such inconvenience, the slinger 22 (fixed portion 22a and disc portion 22b) is deformed at the time of fitting to the raceway ring (for example, the rotating wheel 10 (inner ring component 16)). Various measures have been taken to prevent it. For example, Patent Documents 2 and 3 disclose a slinger structure in which the rigidity of a continuous portion (bent portion) between a fixed portion and a disc portion of the slinger is greatly reduced as compared with the fixed portion and the disc portion. .
JP 2003-130075 A JP 2002-147474 A JP 2006-046628 A

  However, merely reducing the rigidity of the slinger bending portion in this way reduces the rigidity, that is, the strength of the slinger itself, which is not always a good idea. In particular, in a hub unit bearing (for example, bearing unit A shown in FIG. 3 (a)) for supporting automobile wheels, not only muddy water but also solids such as stepping stones and vigorous splashing are applied to the slinger of the pack seal. Since the function of protecting the bearing from an object having a large impulse, such as water, is required, a structure that greatly reduces the rigidity of the slinger bending portion and reduces the strength of the slinger It is not preferable.

  The present invention has been made in order to solve such a problem, and an object of the present invention is to prevent deformation of the sealing device at the time of fitting to the bearing device without reducing the strength of the sealing device. Another object of the present invention is to provide a mounting structure for a bearing sealing device that can maintain a certain sealing performance.

In order to achieve such an object, the mounting structure for a bearing sealing device according to the present invention is incorporated into at least a pair of bearing rings opposed to each other so as to be relatively rotatable, and to be able to roll between the bearing rings. In a bearing device comprising a plurality of rolling elements and a sealing device for keeping the inside airtight and liquid-tight, it is an attachment structure for fixing the sealing device to any of the race rings, A cylindrical fixed portion extending in a predetermined direction from the proximal end to the distal end, and a disc portion continuous with the proximal end of the fixed portion and extending at a predetermined angle with respect to the fixed portion, Any one of the race rings is provided with at least an annular slinger to which the fixing portion is fixed.
Then, the slinger protrudes over the entire circumference toward the raceway where the slinger is thicker than the other part in the middle part between the proximal end and the distal end of the fixed part and the slinger is fixed. The protrusion part is provided, and the protrusion part is fixed in contact with the raceway.
In the present invention, the continuous portion of the fixed portion and the disc portion is set to be thinner than the thickness of the fixed portion excluding the protruding portion, and the continuous portion is thinned by being stretched by press working.

The present invention relates to at least a pair of bearing rings arranged so as to be capable of relative rotation, a plurality of balls incorporated so as to roll between the raceways of the bearing rings, and a seal for keeping the inside airtight and liquid-tight. A ball bearing provided with a device, wherein the sealing device is a mounting structure for a bearing sealing device for fixing the sealing device to any one of the bearing rings, and the sealing device extends in a predetermined direction from a proximal end to a distal end. Consisting of a cylindrical fixing part and a base part of the fixing part and extending at a predetermined angle with respect to the fixing part, the fixing part is fixed to one of the race rings. A ring slinger that is fixed to the ring, and a portion of the race ring that is fixed between the base end and the tip end of the slinger fixing portion is fixed to the slinger. Project all around the part A protruding portion is provided, and the protruding portion has a width that does not reach the groove shoulder of the raceway surface, and is formed by grinding at the same time as the raceway surface. The slinger is fixed by contacting a midway portion between the tip and the tip.

  According to the mounting structure for a bearing sealing device of the present invention, it is possible to prevent deformation of the sealing device during fitting to the bearing device without reducing the strength of the sealing device. As a result, the durability of the sealing device can be increased to improve the sealing performance, and the sealing performance of the bearing device can be kept constant over a long period of time.

  The bearing sealing device mounting structure of the present invention will be described below with reference to the accompanying drawings. The bearing sealing device mounting structure according to the present invention can be applied as a structure for mounting a sealing device for keeping the inside of various bearing devices airtight and liquid-tight (sealed), Here, the case where it is used as an attachment structure of the sealing device which seals the inside of the hub unit bearing (bearing unit A) for supporting the wheel of an automobile as shown in FIG. In this case, the case where the said sealing device is attached to the vehicle body inner side (right side of Fig.3 (a)) of a motor vehicle is assumed as an example. Further, in the following description, for the sake of convenience, the vehicle body inner side (right side in FIG. 3A) to which the sealing device is attached is referred to as the inboard side, and the opposite side, that is, the vehicle body outer side. The side (wheel side (left side in the figure)) is called the outboard side.

  FIG. 3 (a) shows the driving wheels of an automobile (rear wheels of a front engine rear wheel drive (FR) car and rear engine rear wheel drive (RR) car, front engine front wheel drive (FF) car). The configuration of a hub unit bearing that supports front wheels and all wheels of a four-wheel drive (4WD) vehicle is shown as an example, but the bearing unit is a driven wheel of an automobile (a front wheel of an FR car and an RR car, an FF car) You may comprise as a hub unit bearing which supports a rear wheel.

  The type (type) of the bearing unit is not particularly limited. For example, the presence / absence and number of flanges 14f of the rotating wheel 10 (hub 14), the presence / absence and number of flanges 12f of the stationary ring 12, or the presence / absence of the inner ring component 16 The type of rolling element 18 (balls and various rollers) may be arbitrarily set according to the usage conditions and purpose of the bearing unit. Further, in the configuration shown in FIG. 3 (a), the outer member (outer raceway) is the stationary ring 12, and the inner member (inner raceway) is the rotary wheel 10 (hub 14 and inner ring component 16). However, on the contrary, a bearing unit having a configuration in which the outer member (outer race ring) is a rotating ring and the inner member (inner race ring) is a stationary ring may be used.

The inner ring constituting body 16 is formed with a raceway surface 10i that faces the raceway surface 12o on the inboard side of the stationary wheel 12, and is fitted on the inboard side of the hub 14 to constitute the rotating wheel 10 together with the hub 14. It refers to a member.
In any of the bearing units described above, the rotating wheel 10 has a wheel component member (for example, a disc wheel (not shown)) fixed and rotating together with the wheel component member, whereas the stationary wheel 12 The vehicle body component (for example, a knuckle (not shown) of the suspension device) is fixed and kept stationary.

  FIGS. 1A and 1B show a bearing sealing device (hereinafter also simply referred to as a sealing device) 6 according to a first embodiment of the present invention, and its mounting structure. Is a bearing unit A as shown in FIG. 3 (a), that is, a plurality of rolling rings 10 and 12, which are arranged to face each other so as to be relatively rotatable, The inside of the wheel support bearing unit (hub unit bearing) provided with the moving body (ball) 18 is shielded from the outside, and the inside is kept in a sealed state (airtight state and liquid tight state). Specifically, as the races 10 and 12, a stationary wheel 12 fixed to a vehicle body component (for example, a knuckle (not illustrated) of a suspension device) and a wheel component (for example, a disc wheel (not illustrated)) are provided. The rotating wheels 10 that are fixed and rotate together with the wheel constituent members are opposed to each other so as to be relatively rotatable, and are formed on the stationary wheel 12 and the rotating wheel 10, respectively, and between the track surfaces 10 i and 12 i that face each other, and the track. A plurality of rolling elements (balls) 18 are incorporated between the surfaces 10o and 12o so as to be able to roll, thereby forming a bearing unit A.

  In this case, the stationary wheel 12 is integrally formed with a fixing flange 12f that protrudes outward (in the diameter expansion direction) from the outer peripheral surface 12a, and a fixing bolt is inserted into the fixing hole 12h that passes through the fixing flange 12f. By inserting (not shown) and fastening it to the vehicle body side, the stationary wheel 12 can be fixed to a knuckle of a suspension device (suspension) not shown.

  On the other hand, the rotating wheel 10 is provided with a hub 14 having a substantially cylindrical shape, and the hub 14 is fixed to a disk wheel (not shown) of a wheel via a brake rotor (not shown) of a brake. It is configured to rotate with the disc wheel. Note that a hub flange 14f for fixing (externally fitting) the brake rotor and the disc wheel to the outboard side of the hub 14 projects continuously along the circumferential direction.

  The hub flange 14f extends outward (in the direction of diameter expansion of the hub 14) beyond the stationary ring 2, and a plurality of through holes (bolt holes) are provided in the vicinity of the extended edge along the circumferential direction. 14h is provided. A brake rotor and a disc wheel (not shown) are each provided with a plurality of through holes (as an example, the same number as the bolt holes 14h) that can communicate with the bolt holes 14h. Then, the brake rotor and the disc wheel can be positioned and fixed with respect to the hub flange 14f by inserting the hub bolt 14b from the bolt hole 14h into the through hole and fastening (tightening) with a hub nut (not shown). it can.

The hub 14 is configured such that a substantially cylindrical inner ring component 16 is externally fitted on the inboard side. For example, a plurality of rolling elements (balls) are provided between the stationary ring 12 and the hub 14. 18, after the inner ring component 16 is applied to the stepped portion 14 s formed on the hub 14, the inboard side end portion (the right end in FIG. 3A) of the hub 14 is crimped, The inner ring component 16 can be fixed to the inboard side of the hub 14, and a predetermined preload can be applied to the bearing unit A (more specifically, the rolling elements (balls) 18).
Instead of the above-described caulking and fixing, for example, after the inner ring component 16 is externally fitted to the stepped portion 14s formed on the hub 14, it is tightened by a fastening member such as a nut from the inboard side. The inner ring component 16 may be fixed to the inboard side of the hub 14 in some cases.

In the configuration shown in FIG. 3A, the rolling elements (balls) 18 are rotatably held between the raceway surfaces 10i and 12i in a pocket formed in the annular cage 17 one by one. It is incorporated between the raceway surfaces 10o and 12o and rolls between them at a predetermined interval (for example, an equal interval).
Thereby, each rolling element (ball) 18 can smoothly roll between the raceway surfaces 10i and 12i and between the raceway surfaces 10o and 12o without the rolling surfaces coming into contact with each other. It is possible to prevent an increase in rotational resistance or seizure caused by friction between the rolling elements (balls) 18 that come into contact with each other. At that time, it is preferable to enclose a lubricant (as an example, grease) inside the bearing unit A in order to more effectively prevent such an increase in rotational resistance and seizure.

  In addition, what is necessary is just to apply arbitrary types as a holder | retainer according to the kind of rolling element. For example, when the rolling element is a ball 18, an inclined type (FIG. 3A) or a crown type can be applied, and the rolling element can be various types of rollers (such as a tapered roller, a cylindrical roller, and a spherical roller). In this case, types such as a punching die, a comb die and a cage die can be applied.

  In this embodiment, as shown in FIGS. 1 (a) and 1 (b), the sealing device 6 has a cylindrical shape extending from the base end ab to the tip at (from the right end to the left end in each figure) in a predetermined direction. Consisting of a fixed portion 62a and a base end ab of the fixed portion 62a and a disk portion 62b extending at a predetermined angle with respect to the fixed portion 62a, the rotating wheel 10 (specifically, the inner ring configuration) It comprises at least an annular slinger 62 fixed to the body 16).

  In the configuration shown in FIG. 1 (a), the sealing device 6 (slinger 62) has a fixed portion 62a fitted in a predetermined length (the left-right direction in FIG. 1) with a predetermined length (rotating wheel 10 (inner ring component 16) fitting. It is formed in a cylindrical shape extending with the width of the surface 10s (distance in the same direction in the figure), and the disc part 62b has a predetermined length (rotation) substantially perpendicular to the fixed part 62a. The diameter increasing direction is continuous with the base end ab of the fixing portion 62a at a distance (smaller than the vertical distance in FIG. 3A) between the ring 10 (inner ring structure 16) and the stationary ring 12. It is formed in an annular flat plate shape (ring plate shape) extending in the upward direction of FIG. That is, in this case, the slinger 62 is configured such that the longitudinal cross-sectional shape is substantially L-shaped.

  Note that the size (extension length, wall thickness (distance in the vertical direction in FIG. 1A) and diameter dimension, etc.) of the fixed portion 62a, and the size (extension length, wall thickness) of the disc portion 62b are also shown. (Distance in the left-and-right direction in the figure) and diameter dimensions) of the rotating wheel 10 (inner ring component 16) so that it can rotate with the rotating wheel 10 (inner ring component 16) of the bearing unit A, for example. Since it may be arbitrarily set according to the size and shape, there is no particular limitation here. Further, the angle of inclination of the disc portion 62b with respect to the fixed portion 62a is not particularly limited, and may be arbitrarily set according to the use conditions of the sealing device 6 (slinger 62).

  Further, the material and forming method of the slinger 62 are not particularly limited. For example, the slinger 62 is made of a predetermined metal plate (steel plate), and the slinger 62 is formed by pressing the metal plate (steel plate). That's fine. For example, when the slinger 62 is made of stainless steel, when the sealing device 6 has a package structure (pack seal) described later, the sliding contact surface with the lip 261 of the seal 26 (see the dotted circle in FIG. 3A). Rusting is prevented from occurring on the outer peripheral surface of the fixing portion 62a (the upper surface in FIG. 1A) and the inner surface of the disk portion 62b (the left surface in FIG. 1). It is possible to effectively prevent the lip 26l from being damaged at the time of contact.

The slinger 62 has a portion where the fixing portion 62a is closer to the tip at than the base end ab is thicker than the other portions, and all of the slinger 62 faces the rotating wheel 10 (inner ring structure 16) to which the slinger 62 is fixed. A projecting portion 70 that protrudes over the circumference is provided, and the projecting portion 70 is fixed in contact with the rotating wheel 10 (the inner ring constituting body 16).
In the configuration shown in FIGS. 1A and 1B, the inner diameter dimension of the intermediate portion between the base end ab and the distal end at of the fixing portion 62a is set to the width W with respect to the extending direction of the fixing portion 62a. The projecting portion 70 is formed by reducing the diameter and reducing the diameter over the entire circumference by the height H from the inner peripheral surface as of the fixed portion 62a. As a result, the slinger 62 has the fixing portion 62a thicker at the protruding portion 70 than the other portions by the height H, and the protruding portion 70 is directed toward the rotating wheel 10 (inner ring structure 16) by the height H. It becomes a projecting structure.

By making the slinger 62 such a structure, when the slinger 62 is fitted and fixed to the rotating wheel 10 (inner ring structure 16), the fixing portion 62a is only the protruding portion 70 and the rotating wheel 10 is fixed. It abuts on the fitting surface 10s of the (inner ring component 16). That is, at the time of such a fitting, the fitting position between the slinger 62 and the rotating wheel 10 (inner ring constituting body 16) is a position where the fixing part 62a is not easily affected by the rigidity against the hoop stress of the disk part 62b of the slinger 62. Can be far away. As a result, it is possible to keep the rigidity of the fixing portion 62a and the disc portion 62b with respect to the hoop stress generated when the slinger 62 is fitted substantially uniform.
Therefore, when the slinger 62 is fitted, for example, deformation such that the disk portion 62b is tilted forward with respect to the fitting direction of the slinger 62, or deformation in the diameter-expanding direction where the tip portion of the fixed portion 62a is lifted. And the like, and the strength of the slinger 62 can be increased.

  As described above, according to the mounting structure of the bearing sealing device according to the present embodiment, specifically, the fitting structure of the slinger 62, the durability against deformation of the slinger 62 is enhanced and the sealing performance (airtightness and liquid tightness) is improved. 3), and by attaching (fitting) the slinger 62 to the rotating wheel 10 (inner ring component 16) with the mounting structure, the sealing performance of the bearing unit A (FIG. 3A). Can be kept constant over a long period of time.

Here, since the form (size (size of width W or height H), shape, etc.) of the protruding portion 70 of the fixing portion 62a may be arbitrarily set according to the size, shape, etc. of the slinger 62, particularly It is not limited.
For example, in the configuration shown in FIGS. 1A and 1B, the protruding portion 70 is protruded toward the rotating wheel 10 (inner ring component 16) with a width W that does not reach the tip at of the fixed portion 62a. However, the protruding portion 70 may protrude toward the rotating wheel 10 (inner ring structure 16) with a predetermined width reaching the tip at of the fixing portion 62a. In this case, a step (see FIGS. 1A and 1B) is not formed on the distal end at side of the fixed portion 62a, and the distal end at side of the protruding portion 70 is substantially flush with the distal end at side of the fixed portion 62a. Composed.

However, the width W of the protruding portion 70 is about one third (W≈L / 3) of the extension dimension of the fixing portion 62a (the distance L from the base end ab to the tip at shown in FIG. 1B). It is preferable to set. For example, when the extension dimension L of the fixing portion 62a is about 1.5 to 6.0 mm, the width W of the protruding portion 70 may be set to about 0.5 to 2.0 mm.
Moreover, what is necessary is just to set the height H of the protrusion part 70 to about 0.03-0.1 mm.

  In this case, the slinger 62 is provided with a fitting allowance for fitting to the rotating wheel 10 (inner ring constituting body 16) with respect to the inner diameter dimension (specifically, the inner diameter dimension of the protruding portion 70). May be. That is, the slinger 62 has an inner diameter dimension of the projecting portion 70 that is equal to the fitting allowance than the outer diameter dimension of the rotating wheel 10 (inner ring structure 16) (specifically, the diameter dimension of the fitting surface 10s). Can be configured with small dimensions. At this time, the fitting allowance to be set in the protruding portion 70 may be arbitrarily set according to the size of the rotating wheel 10 (inner ring constituting body 16).

Also, the method for forming the protruding portion 70 is not particularly limited. For example, when the slinger 62 is formed by press working, the protruding portion 70 is simultaneously formed on the fixed portion 62a simultaneously with the forming of the slinger 62. Can do.
At this time, the position where the projecting portion 70 is formed with respect to the fixing portion 62a is determined by the effect of rigidity on the hoop stress of the disc portion 62b when the slinger 62 is fitted to the rotating wheel 10 (inner ring constituting body 16). The position where the fixing portion 62a can be moved to a position where the fixing portion 62a is difficult to receive, if viewed in another way, the rigidity of the fixing portion 62a and the disc portion 62b with respect to the hoop stress generated when the slinger 62 is fitted is apparently substantially uniform. It may be set in accordance with the size or material of the slinger 62 at a position where it can be maintained.

  In the configuration shown in FIGS. 1A and 1B, as an example, the thicknesses of the fixing portion 62a and the disc portion 62b of the slinger 62 are set to be substantially uniform except for the protruding portion 70. By providing the protruding portion 70 with respect to the fixing portion 62, the rigidity of the fixing portion 62a against hoop stress can be increased, and the apparent uniformity with the rigidity of the disc portion 62b can be maintained. Therefore, as in the modification shown in FIG. 2A, a continuous portion (hereinafter referred to as a bent portion) 72 between the fixing portion 62 a and the disc portion 62 b within a range in which the rigidity (strength) of the entire slinger 62 can be ensured. May be set to be thinner than the thickness of the fixing portion 62a and the disc portion 62b excluding the protruding portion 70.

  At this time, the method for forming the bent portion 72, which is a thin-walled portion, with respect to the slinger 62 is not particularly limited. After the molding is performed, the bending portion 72 can be made thinner than other portions by performing predetermined machining (turning or cutting) on the slinger 62 after the molding. If the bent portion 72 is extended by a press machine or the like, the processing efficiency is good, and the thickness of the bent portion 72 can be made thinner than other portions more easily.

  For example, when burring is generally performed with a press machine, the punch radius rp and the diradius rd may be set to rp = rd within 4 to 6 times or more and 10 to 20 times the plate thickness. In many cases, when the relationship of rp <rd is set, the punch hooks the chamfered portion (R stop) slightly on the chamfered portion (R stop) of the bent portion 72 and the chamfered portion (R stop). The thickness of the bent portion 72 can be made thinner than other portions by stretching the meat in the vicinity of the portion.

Moreover, in this embodiment (1st Embodiment) mentioned above and its modification, by providing the protrusion part 70 with respect to the slinger 62, the fixing | fixed part 62a of the said slinger 62 is used for the rotary wheel 10 (inner ring structure 16). ) Is projected toward the fitting surface 10s. For example, the mounting structure of the bearing sealing device according to the second embodiment of the present invention shown in FIG. A fitting structure (fitting structure) in which the fitting surface 10s side of the rotating wheel 10 (inner ring constituting body 16) protrudes toward the fixing portion 62a of the slinger 62 may be used.
In this case, as shown in FIG. 2B, the peripheral portion of the fitting surface 10 s is protruded over the entire circumference toward the fixed portion 62 a of the slinger 62 on the rotating wheel 10 (inner ring component 16). A projecting portion 80 is provided, and the slinger 62 is fixed by contacting the projecting portion 80 with a portion closer to the distal end at than the base end ab of the fixing portion 62a of the slinger 62.

  More specifically, the fitting surface 10 s of the rotating wheel 10 (inner ring structure 16) facing a midway portion between the base end ab and the tip at of the fixing portion 62 a of the slinger 62 has a predetermined width (FIG. 1 (b) corresponding to the width W of the projecting portion 70) and the entire circumference of the fitting surface 10s by a predetermined height (corresponding to the height H of the projecting portion 70). The protruding portion 80 is formed by expanding the diameter. Thereby, the rotating wheel 10 (inner ring structure 16) is a structure in which the fitting surface 10s protrudes the protruding portion 80 by a predetermined height from the other portion toward the fixing portion 62a of the slinger 62.

  By making the rotating wheel 10 (inner ring structure 16) such a structure, when the slinger 62 is fitted and fixed to the rotating wheel 10 (inner ring structure 16), the fixing portion 62a of the slinger 62 is The contact surface 10s of the rotating wheel 10 (inner ring structure 16) is in contact with the protruding portion 80 only. That is, at the time of such fitting, the fitting position of the slinger 62 with the rotating wheel 10 (inner ring constituting body 16) is closer to the distal end at (the proximal end) than the proximal end ab of the fixed portion 62a abutted against the protruding portion 80. a halfway between ab and tip at). Therefore, as in the case of the first embodiment described above, the fitting position between the slinger 62 and the rotating wheel 10 (inner ring constituent body 16) is set to the effect of rigidity on the hoop stress of the disk portion 62b of the slinger 62. As a result, the rigidity of the fixing portion 62a and the disc portion 62b against the hoop stress generated when the slinger 62 is fitted can be kept substantially uniform.

Here, the shape (size (size of width and height), shape, etc.) of the protruding portion 80 of the fitting surface 10s is the protruding portion 70 of the fixing portion 62a of the slinger 62 described above (FIG. 1 (a), ( Similarly to b)), the slinger 62 may be arbitrarily set according to the size and shape of the slinger 62 and is not particularly limited.
For example, in the configuration shown in FIG. 2 (b), the projecting portion 80 has a width that does not reach the groove shoulder of the raceway surface 10i formed on the rotating wheel 10 (inner ring constituent body 16) to the fixing portion 62a of the slinger 62. However, the protruding portion 80 may protrude toward the fixed portion 62a with a predetermined width reaching the groove shoulder of the raceway surface 10i. In this case, a step (see FIG. 2B) is not formed on the groove shoulder side of the fitting surface 10s, and the groove shoulder side of the protruding portion 80 is configured to be continuous with the track surface 10i.

  However, the width of the protruding portion 80 is preferably set to about one third of the extension dimension L of the fixing portion 62a, like the width W of the protruding portion 70. For example, when the extension dimension L of the fixed portion 62a is about 1.5 to 6.0 mm, the width of the protruding portion 80 may be set to about 0.5 to 2.0 mm. Similarly, the height of the protruding portion 80 may be set to about 0.03 to 0.1 mm.

  In this case, the slinger 62 is provided with a fitting allowance for fitting to the rotating wheel 10 (inner ring component 16) with respect to the inner diameter dimension (specifically, the inner diameter dimension of the fixed portion 62a). May be. That is, the slinger 62 has an inner diameter dimension of the fixing portion 62a larger than the outer diameter dimension of the rotating wheel 10 (inner ring structure 16) (specifically, the diameter dimension of the protruding portion 80 of the fitting surface 10s). The size can be set to be as small as the cost. At this time, the fitting allowance set for the fixing portion 62a may be arbitrarily set according to the size of the protruding portion 80 or the like.

  Further, the method for forming the projecting portion 80 is not particularly limited. However, when grinding is performed on the raceway surface 10i of the rotating wheel 10 (inner ring structure 16), the same grinding process is performed on the fitting surface 10s at the same time. By applying, the projecting portion 80 can be formed on the fitting surface 10s simultaneously with the formation of the track surface 10i.

  In general, the fitting surface 10s (projecting portion 80) of the slinger 62 is often ground integrally with the raceway surface 10i using a grindstone formed of a diamond wheel. At that time, the vicinity of the groove shoulder of the raceway surface 10i has a large crossing angle between the rotation axis of the grindstone and the grinding surface, so that the grindstone is not sharp. In addition, it is difficult to supply coolant because grinding is performed at the concave portion of the grindstone. Such problems are likely to occur. Further, the grinding speed for the rotating wheel 10 (inner ring component 16) is often influenced by the grinding situation near the groove shoulder.

  In the present embodiment, as shown in FIG. 2 (b), only the part facing the middle part between the base end ab and the tip at of the fixing part 62a protrudes toward the fixing part 62a. Since the protruding portion 80 is formed with respect to the fitting surface 10s, the vicinity of the groove shoulder of the raceway surface 10i of the rotating wheel 10 (inner ring structure 16) is fitted (contacted) with the slinger 62 (fixed portion 62a). Therefore, it is not necessary to grind the vicinity of the groove shoulder. Therefore, since the coolant supply state can be remarkably improved at the time of grinding, the grinding speed for the rotating wheel 10 (inner ring constituent body 16) is improved and the grinding cost can be reduced. be able to.

  In this case, when the slinger 62 is fitted to the protruding portion 80, the position where the protruding portion 80 is formed with respect to the fitting surface 10s is set to the fitting position (that is, the position where the protruding portion 80 is formed) of the disc portion 62b. The position where the fixing portion 62a can be moved away to the position where the fixing portion 62a is difficult to receive the influence of the rigidity on the hoop stress, if viewed in another way, the fixing portion 62a and the disc portion 62b against the hoop stress generated when the slinger 62 is fitted. What is necessary is just to set according to the magnitude | size, material, etc. of the slinger 62 in the position which can maintain rigidity substantially apparently.

In the above-described first embodiment of the present invention, the modification thereof, and the second embodiment, the sealing device 6 has been described as a single structure of the slinger 62. However, the configuration of the sealing device 6 has such a slinger single structure. It is not limited to.
For example, the sealing device 6 includes a package structure (so-called pack seal), that is, a slinger 62 (FIGS. 1A and 1B and FIGS. 2A and 2B), a core bar (FIG. 3A). A structure in which a seal core metal 24 as shown in a dotted circle and a seal (corresponding to the seal 26 in the figure) are combined may be used.

In this case, the pack seal is continuous with the slinger 62, the cylindrical metal core fixing part extending in a predetermined direction from the base end to the front end, and the base end of the metal core fixing part, and the pack seal is attached to the metal core fixing part. An annular cored bar made of a cored bar disk extending at a predetermined angle with respect to the slinger 62 and the cored bar, connected to one of the slinger 62 and the cored bar, and the other A seal that comes into sliding contact is provided. Then, the sealing device 6 may be configured by combining the slinger 62, the cored bar, and the seal so that the contour shape of the cross section is substantially rectangular (as shown in the dotted circle in FIG. 3A). A similar configuration in which only the configuration of the pack seal 2 and the slinger 62 differs.
By making the sealing device 6 have such a package structure (pack seal), its sealing performance (airtight performance and liquid tight performance) can be remarkably enhanced.

Further, for example, the disk portion 62b of the slinger 62 is used as a detection object of a sensor (not shown) that detects the rotation state of the slinger 62 (specifically, the rotating wheel 10 (inner ring component 16)). An encoder (not shown) may be attached. In this case, as an example, a sensor as a detection body is a magnetic sensor, and a magnetic pole body (sensor encoder (not shown)) made of a predetermined magnetic material magnetized in multiple poles is used as a detection body of the magnetic sensor. The slinger 62 can be configured by being attached to the plate portion 62b.
Thus, a bearing unit having a sensor function capable of measuring the rotation state (for example, rotation speed, rotation angle or rotation direction) while keeping the inside in a sealed state (airtight state and liquid-tight state). It can be configured. In this case, the slinger 62 is configured as the sealing device 6 and is also configured as a core metal (that is, an encoder core metal) for attaching a magnetic pole body (sensor encoder (not shown)).

  As described above, according to the mounting structure for a bearing sealing device according to the present invention (for example, the fitting structure of the slinger 62), the bearing device (for example, a bearing unit) is obtained without reducing the strength of the sealing device (slinger 62). The deformation of the sealing device (slinger 62) at the time of fitting to A (FIG. 3 (a)) can be prevented. As a result, the durability of the sealing device (slinger 62) can be improved to improve the sealing performance (airtight performance and liquid tightness performance), and the sealing performance of the bearing device (bearing unit A) can be maintained over a long period of time. You can keep on.

BRIEF DESCRIPTION OF THE DRAWINGS It is a figure which shows the attachment structure of the sealing device for bearings which concerns on 1st Embodiment of this invention, Comprising: (a) is principal part sectional drawing which shows the state which fitted the slinger to the rotating wheel (inner ring structure), (b) is sectional drawing which shows the structure of a slinger (projection site | part). (a) is sectional drawing which shows the attachment structure of the sealing device for bearings concerning the modification of 1st Embodiment, (b) is a cross section which shows the attachment structure of the sealing device for bearings concerning 2nd Embodiment of this invention Figure. It is a figure which shows the attachment structure of the conventional sealing device for bearings, Comprising: (a) is sectional drawing of the bearing unit (hub unit bearing) to which the pack seal was attached (the dotted line circle is an important section expanded section of the pack seal) (FIGS.), (B) and (c) are cross-sectional views showing a deformed state when the slinger is fitted.

Explanation of symbols

6 (62) Sealing device (Slinger)
10 (16) Rotating wheel (inner ring component)
62a fixed part 62b disc part 70 protrusion part ab fixed part base end at fixed part tip

Claims (3)

A bearing device comprising at least a pair of bearing rings arranged so as to be capable of relative rotation, a plurality of rolling elements incorporated so as to be able to roll between the bearing rings, and a sealing device for keeping the inside airtight and liquid-tight. In the mounting structure of the bearing sealing device for fixing the sealing device to any of the bearing rings,
The sealing device includes a cylindrical fixing portion extending in a predetermined direction from a base end to a tip end, and a disc portion extending at a predetermined angle with respect to the fixing portion while continuing to the base end of the fixing portion. Comprising at least an annular slinger to which the fixed portion is fixed to any one of the race rings,
The slinger is thicker than the other part in the middle part between the proximal end and the distal end of the fixed part , and protrudes over the entire circumference toward the race ring to which the slinger is fixed. A bearing sealing device mounting structure comprising a portion, wherein the protruding portion is fixed in contact with the raceway ring. The continuous portion of the fixed portion and the disc portion is set to be thinner than the thickness of the fixed portion excluding the protruding portion, and the continuous portion is thinned by stretching by press working. The mounting structure for a bearing sealing device according to claim 1. At least a pair of bearing rings arranged so as to be capable of relative rotation, a plurality of balls incorporated so as to roll between the raceways of the bearing rings , and a sealing device for keeping the inside airtight and liquid-tight. In the ball bearing , the bearing sealing device mounting structure for fixing the sealing device to any of the raceway,
The sealing device includes a cylindrical fixing portion extending in a predetermined direction from a base end to a tip end, and a disc portion extending at a predetermined angle with respect to the fixing portion while continuing to the base end of the fixing portion. Comprising at least an annular slinger to which the fixed portion is fixed to any one of the race rings,
In the raceway ring to which the slinger is fixed, a protrusion that protrudes over the entire circumference toward the fixing part of the slinger, with a part facing the intermediate part between the base end and the tip of the fixing part of the slinger sites are provided, and the projecting portion is by no width reaching groove shoulder of the raceway surface is formed by simultaneously grinding track surface, proximal and distal ends of the fixing portion of the slinger to the projecting portion A structure for mounting a sealing device for a bearing, wherein the slinger is fixed by abutting a midway portion therebetween .

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