CN203189534U - Rolling bearing unit for wheel support - Google Patents

Rolling bearing unit for wheel support Download PDF

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Publication number
CN203189534U
CN203189534U CN2013202397558U CN201320239755U CN203189534U CN 203189534 U CN203189534 U CN 203189534U CN 2013202397558 U CN2013202397558 U CN 2013202397558U CN 201320239755 U CN201320239755 U CN 201320239755U CN 203189534 U CN203189534 U CN 203189534U
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CN
China
Prior art keywords
wheel
ring
axial
race track
outer ring
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Fee Related
Application number
CN2013202397558U
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Chinese (zh)
Inventor
盐野泰宏
石川宽朗
高山明伸
高山幸久
高梨晴美
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NSK Ltd
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NSK Ltd
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Filing date
Publication date
Priority claimed from JP2013038076A external-priority patent/JP2014142054A/en
Application filed by NSK Ltd filed Critical NSK Ltd
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Publication of CN203189534U publication Critical patent/CN203189534U/en
Anticipated expiration legal-status Critical
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/72—Sealings
    • F16C33/76—Sealings of ball or roller bearings
    • F16C33/78—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members
    • F16C33/7869—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted with a cylindrical portion to the inner surface of the outer race and having a radial portion extending inward
    • F16C33/7873—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted with a cylindrical portion to the inner surface of the outer race and having a radial portion extending inward with a single sealing ring of generally L-shaped cross-section
    • F16C33/7876—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted with a cylindrical portion to the inner surface of the outer race and having a radial portion extending inward with a single sealing ring of generally L-shaped cross-section with sealing lips
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
    • F16C19/18—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls
    • F16C19/181—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact
    • F16C19/183—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles
    • F16C19/184—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles in O-arrangement
    • F16C19/186—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles in O-arrangement with three raceways provided integrally on parts other than race rings, e.g. third generation hubs
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/58—Raceways; Race rings
    • F16C33/64—Special methods of manufacture
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/72—Sealings
    • F16C33/76—Sealings of ball or roller bearings
    • F16C33/78—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members
    • F16C33/7869—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted with a cylindrical portion to the inner surface of the outer race and having a radial portion extending inward
    • F16C33/7879—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted with a cylindrical portion to the inner surface of the outer race and having a radial portion extending inward with a further sealing ring
    • F16C33/7883—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted with a cylindrical portion to the inner surface of the outer race and having a radial portion extending inward with a further sealing ring mounted to the inner race and of generally L-shape, the two sealing rings defining a sealing with box-shaped cross-section
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/72—Sealings
    • F16C33/76—Sealings of ball or roller bearings
    • F16C33/80—Labyrinth sealings
    • F16C33/805—Labyrinth sealings in addition to other sealings, e.g. dirt guards to protect sealings with sealing lips
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
    • F16C19/18—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls
    • F16C19/181—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact
    • F16C19/183—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles
    • F16C19/184—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles in O-arrangement
    • F16C19/187—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles in O-arrangement with all four raceways integrated on parts other than race rings, e.g. fourth generation hubs
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2220/00—Shaping
    • F16C2220/60—Shaping by removing material, e.g. machining
    • F16C2220/70—Shaping by removing material, e.g. machining by grinding
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2326/00—Articles relating to transporting
    • F16C2326/01—Parts of vehicles in general
    • F16C2326/02—Wheel hubs or castors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/66—Special parts or details in view of lubrication
    • F16C33/6603—Special parts or details in view of lubrication with grease as lubricant

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Manufacturing & Machinery (AREA)
  • Rolling Contact Bearings (AREA)

Abstract

The utility model provides a rolling bearing unit for wheel support. The rolling bearing unit can improve the sealing performance of a sealing ring under the condition of not increasing the rotating resistance, can further improve the effect of preventing foreign materials from entering a rotating body installing space, and has excellent durability. The rolling bearing unit is formed by approaching and oppositely placing the top end parts of a labyrinth sealing lip (33) and the inner side surface of a rotating side flange (12) on the whole circumference, so the labyrinth sealing is formed. Compared with the outer circumference edge of the outer end surface of an outer ring (2), the outer diameter edge of a round wheel part (35) of a sealing ring (14) is projected towards the outer side of the radial direction, urea type lubricating grease or lubricating grease with the same composition as the lubricating grease filled into an internal space (15) for lubrication is coated on a sealing lip (32), and in addition, lubricating grease is not coated on the labyrinth sealing lip (33).

Description

Wheel-support rolling bearing unit
Technical field
The utility model relates to a kind of improvement of wheel-support rolling bearing unit, and this wheel-support rolling bearing unit is used for automotive wheel is supported on draft hitch.Particularly, the utility model can be realized a kind of wheel-support rolling bearing unit, it can improve the sealability of seal ring under the situation that does not increase rotational resistance, prevent that foreign matter from entering the effect that rotor arranges the space thereby improve, and have IMAGE.
Background technique
Automotive wheel is for example shown in Figure 20, and the wheel-support rolling bearing unit 1 by possessing seal ring 14 is supported on the draft hitch with free rotation mode.This wheel-support rolling bearing unit 1 sees through a plurality of rotors 4,4 and wheel hub 3 is supported on the internal side diameter of outer ring 2 with free rotation mode.Wherein, outer ring 2 is provided with for the Stationary side flange 5 that it is supported and fixed on the draft hitch at its outer circumferential face, and side face is provided with multiple row outer race track 6,6 within it.And, be formed with a plurality of mounting holes 18 on the described Stationary side flange 5, by with screw threaded on described each mounting hole 18, just on the draft hitch that outer ring 2 support fixation can be shown in the drawings.In addition, described wheel hub 3 makes up fixing formation by nut 9 with hub body 7 and inner ring 8, and is provided with multiple row inner race track 10,10 at its outer circumferential face.In addition, described each rotor 4,4 under the states that kept by retainer 11,11, with the mode of freely rotating be separately positioned on described two inner race tracks 10,10 and described two outer race tracks 6,6 between, and every row are respectively equipped with a plurality of.
In addition, in the part of the close axial outer end of described hub body 7, be provided with rotation side flange 12 by the outstanding part of the axial outer end opening portion of described outer ring 2.These rotation side flange 12 upper supports fixedly have the base end part of a plurality of double-screw bolts 13, by described each double-screw bolt 13, just the wheel support that constitutes wheel can be fixed on the rotation side flange 12.In addition, about axially, the inboard refers to be assembled into the width direction center side (right side of each figure) under the vehicle-state, and the outside refers to be assembled into the width direction outside (left side of each figure) under the vehicle-state.
In addition, between the outer circumferential face of the inner peripheral surface of the axial outer end portion of described outer ring 2 and the axial intermediate portion of described wheel hub 3 seal ring 14 is installed, sealing circle 14 is present between the outer circumferential face of the inner peripheral surface of outer ring 2 and wheel hub 3, and the axial outer end opening portion that will be provided with described a plurality of rotor 4,4 inner space 15 seals.In addition, seal the axial inner ends opening portion of described outer ring 2 by using outer cover 16, thus prevent foreign matters such as rubbish, rainwater from then on inner opening portion enter in the described inner space 15, and prevent that the lubricating grease that are filled in this inner space 15 from leaking into the outside.
For preventing that foreign matter from entering in the described inner space 15, and prevent that the lubricating grease that are filled in this inner space 15 from leaking, need the fully both ends open portion of this inner space 15 of sealing.Especially, enter in the described inner space 15 for preventing the foreign matter of guiding radially inner side along the inner side surface of rotation side flange 12 into, require to have outstanding sealability for the seal ring 14 of the axial outer end opening portion that seals this inner space 15.
Because this situation, the past just always at the seal ring of the axial outer end opening portion that is used for the described inner space 15 of sealing, was designed various structures.For example, put down in writing a kind of seal ring in the patent documentation 1, the sealing circle possesses three sealing lips, and the sealing lip makes the outer circumferential face of the axial intermediate portion of the inner side surface of its tip portion sliding contact rotation side flange on complete cycle or wheel hub.But, when seal ring has this structure, if service condition is abominable, then might can't give play to sufficient sealability.Namely, bigger foreign matters such as the grains of sand can enter from the slit between the axial inner side surface of the axial outer end face of outer ring and rotation side flange, this foreign matter may enter the top edge of the sealing lip that constitutes seal ring and the sliding contacting part of the inner side surface of rotation side flange, produces the inordinate wear equivalent damage at this sliding contacting part.
With respect to this, be to prevent that foreign matter from entering from the slit between the axial inner side surface of the axial outer end face of outer ring and rotation side flange, discloses the structure that partly increases the contact seal lip in the big footpath of combined seal ring side in the patent documentation 2.But when adopting this structure, sealed force moment can increase, thereby can increase the rotational resistance of wheel-support rolling bearing unit.Therefore this structure can cause automobile running performance, oil consumption performance to reduce, so can not be satisfactory.
Patent documentation
Patent documentation 1: Japanese patent laid-open 9-287619 communique
Patent documentation 2: No. 5813675 specification of U. S. Patent
The model utility content
The problem that model utility will solve
The utility model has In view of the foregoing proposed a kind of wheel-support rolling bearing unit, it can improve the sealability of seal ring under the situation that does not increase rotational resistance, further improve preventing that foreign matter from entering the effect that rotor arranges the space, and have IMAGE.
Wheel-support rolling bearing unit of the present utility model has: the outer ring has outer race track on the side face within it; Wheel hub has inner race track with the opposed part of described outer race track in its outer circumferential face, and this wheel hub and described outer ring concentric arrangement; A plurality of rotors, it is arranged between described outer race track and the described inner race track in the mode of freely rotating; Flange, it is arranged in the outer circumferential face of described wheel hub and compares outstanding laterally part with the outer end opening portion of described outer ring; And seal ring, it is used for sealing the outer end opening portion of the inner space between the outer circumferential face of the inner peripheral surface that is present in described outer ring and described wheel hub.
Described seal ring is strengthened and is constituted with the sealing material body that elastic material is made by the arbor of the outer end that is fixed on described outer ring and by arbor, this sealing material body possesses: at least one sealing lip, the inner side surface of its described flange of sliding contact on complete cycle or the outer circumferential face of described wheel hub; And labyrinth seal lip, its therewith sealing lip compare and be set to more close radial outside, and its tip portion is close opposed with the inner side surface of described flange on complete cycle, thereby and the inner side surface of described flange between form labyrinth seal, the lubricating grease that described inner space is filled with to lubricate is provided with and the opposed round wheel part in the exterior edge face of described outer ring at described arbor.
Especially in wheel-support rolling bearing unit of the present utility model, the external diameter edge of described round wheel part is compared to radial outside outstanding with the exterior edge face outer periphery of described outer ring, be coated with the lubricating grease identical with the grease composition of described inner space or urea class lubricating grease on the described sealing lip.Preferably, in described seal ring, uncoated lubricating grease on the described labyrinth seal lip only is coated with described lubricating grease at described sealing lip.
Wheel-support rolling bearing unit of the present utility model according to said structure, can under the situation that does not increase rotational resistance, improve the sealability of seal ring, further improve preventing that foreign matter from entering the effect that rotor arranges the space, and have IMAGE.
Especially in the utility model, owing to make the labyrinth seal lip extend to the axial outside of the sliding contact point of sealing lip, and the tip portion that makes this labyrinth seal lip in the axial inner side surface of rotation side flange with the fast part of peripheral velocity near opposed, therefore can improve the labyrinth seal effect of labyrinth seal lip.In addition, be provided with round wheel part at the arbor that constitutes described seal ring, the outside dimension of this round wheel part is greater than the outside dimension of the outer end outer circumferential face of outer ring, and the exterior edge face outer periphery of outer ring are compared to radial outside outstanding therewith.Therefore can be attached on the outer circumferential face of outer ring, stop moisture to enter described labyrinth seal along the outer circumferential face of this outer ring.Thereby the moisture that can effectively prevent from being attached on the outer circumferential face of outer ring enters in the labyrinth seal.In addition and since not with labyrinth seal lip that the side face of flange contacts on uncoated lubricating grease, so be attached on the labyrinth seal lip after can preventing lubricating grease and mud mixing.And then, when the surface of labyrinth seal lip adopts bright side (even surface) or its surface configuration to have water to the drainage performance of lower guide, can further suppress mud etc. and be attached on the labyrinth seal lip.
In addition, though with must be coated with the lubricating grease that is used for lubricating on the sealing lip of the side face sliding contact of flange, but by the lubricating grease of coating identical with the grease composition that is filled in the inner space (kind of base oil and water-thickening agent is identical), can avoid mixing the lubrication performance deteriorates that causes because of lubricating grease.In addition, if at the outstanding urea class lubricating grease of sealing lip coating water repellency, be attached on the labyrinth seal lip after lubricating grease on the sealing lip leaks into the outside even then be filled in the lubricating grease of inner space or be coated on, also can suppress mud etc. and be attached on the labyrinth seal lip.
Description of drawings
Fig. 1 (a) is the sectional drawing that shows the 1st mode of execution, and Fig. 1 (b) is the profile that shows the 1st mode of execution.
Fig. 2 (a) is the part sectioned view that shows the seal ring of the 1st mode of execution, and Fig. 2 (b) is the part sectioned view that shows the combined seal ring of the 1st mode of execution.
Fig. 3 (a) is the sectional drawing that shows the 2nd mode of execution, and Fig. 3 (b) is the part sectioned view that shows the seal ring of the 2nd mode of execution.
Fig. 4 is the outer ring sectional drawing of the heat treatment hardened layer scope of explanation the 2nd mode of execution.
Fig. 5 is the outer ring sectional drawing of heat treatment hardened layer scope of the variation of explanation the 2nd mode of execution.
Fig. 6 is the sectional drawing that shows the 3rd mode of execution.
Fig. 7 (a) is the part sectioned view that shows the seal ring of the 3rd mode of execution, and Fig. 7 (b) is the part sectioned view that shows the combined seal ring of the 3rd mode of execution.
Fig. 8 is the hub body sectional drawing of the heat treatment hardened layer scope of explanation the 3rd mode of execution.
Fig. 9 shows the sectional drawing of the axial intermediate portion outer circumferential face of the hub body of the 3rd mode of execution being implemented the state of abrasive machining.
Figure 10 is the outer ring sectional drawing of the heat treatment hardened layer scope of explanation the 3rd mode of execution.
Figure 11 shows the sectional drawing of the outer ring inner peripheral surface of the 3rd mode of execution being implemented the state of abrasive machining.
Figure 12 is the profile of the flow chart of the state that only cuts the outer ring variation that shows the 3rd mode of execution.
Figure 13 is the profile of the flow chart of the state that only cuts the outer ring other variation of showing the 3rd mode of execution.
Figure 14 is the sectional drawing that shows the 4th mode of execution.
Figure 15 is the sectional drawing that shows the 5th mode of execution.
Figure 16 is the sectional drawing that shows the 6th mode of execution.
Figure 17 is the sectional drawing that shows the 7th mode of execution.
Figure 18 is the sectional drawing that shows the variation of the 7th mode of execution.
Figure 19 (a) is the sectional drawing that shows the 8th mode of execution, and Figure 19 (b) is the part sectioned view that shows the seal ring of the 8th mode of execution.
Figure 20 shows the sectional drawing of an example of the wheel-support rolling bearing unit of structure in the past.
Embodiment
[the 1st mode of execution]
Fig. 1～2 have shown the 1st mode of execution of the present utility model.In addition, present embodiment is characterised in that, for the moisture on the outer circumferential face that prevents from being attached to outer ring 2 enters the internal side diameter of labyrinth seal lip 33 along the outer circumferential face of this outer ring 2, it has the structure of labyrinth seal lip 33 and round wheel part 35 and the structure that the axial inner ends opening portion of inner space 15 is sealed.Comprise in being configured in of wheel-support rolling bearing unit, structure beyond seal ring 14a and the combined seal ring 17 and action effect and above-mentioned structure in the past shown in Figure 20 are basic identical, therefore omit or simple explanation and the diagram that repeats, will describe at the characteristic of this example below.
Because what exemplify in the present embodiment is the driving wheel (trailing wheel of FR car, RR car, MR car, the front-wheel of FF car, all wheels of 4WD car) the wheel-support rolling bearing unit 1a of usefulness is so be provided with splined hole 19 with the state that axially runs through hub body 7a at the central part of this hub body 7a.After the live axle that shows among the figure inserted splined hole 19, be fixed on the wheel hub 3 by screw etc., just rotatable driving is supported and fixed on the wheel on the wheel hub 3.In addition, shown in Fig. 1 (b), Stationary side flange 5 integral body are general triangular, and three radially outstanding in this Stationary side flange 5 places are formed with mounting hole 18 respectively, and this mounting hole 18 side face within it is formed with internal thread.On the knuckle of the draft hitch that does not show in the pie graph, be provided with penetration hole with described mounting hole 18 positions aligning, by from knuckle side inserting bolt and further fastening after being screwed on the mounting hole 18, thereby outer ring 2 is supported and fixed on the draft hitch.
Between the outer circumferential face of the inner peripheral surface of described outer ring 2 and described wheel hub 3, the axial both ends open that is provided with the inner space 15 of each ball 4 is sealed by seal ring 14a and combined seal ring 17 respectively on complete cycle.Seal the combined seal ring 17 of axial inner ends side opening of inner space 15 shown in Fig. 2 (b), combined by flinger ring 50 and seal ring 51.Flinger ring 50 is by with bending and forming metallic sheets, thereby section is L-shaped, and integral body constitutes circular, and it is made of rotation side cylindrical part 52 and the axial inner ends edge that the rotates side cylindrical part 52 thus rotation side round wheel part 53 to the radial outside bending.This flinger ring 50 be by will rotating the outer close axial inner ends that is embedded in described wheel hub 3 (together constituting the inner ring 8 of this wheel hub 3 with hub body) of side cylindrical part 52 to tighten chimeric mode, thereby be fixed on the wheel hub 3.
In addition, described seal ring 51 possesses arbor 54 and the elastic material 55 that sheet metal is made.This elastic material 55 possesses a plurality of (being exemplified as 3 among the figure) sealing lip 56a, 56b, 56c.In addition, arbor 54 is by with bending and forming metallic sheets, and roughly L shaped thereby section is, integral body constitutes circular, its by Stationary side cylindrical part 57 and thus the axial outer end edge of Stationary side cylindrical part 57 constitute to the Stationary side round wheel part 58 of radially inner side bending.The seal ring 51 that possesses this arbor 54 is by being embedded in the axial inner ends portion of described outer ring 2 to tighten chimeric mode with Stationary side cylindrical part 57, thereby is fixed on this outer ring 2.In addition, under this state, make the axial outer side surface of top edge sliding contact rotation side round wheel part 53 on complete cycle of sealing lip 56a, and make the outer circumferential face of top edge sliding contact rotation side cylindrical part 52 on complete cycle of each sealing lip 56b, 56c.
And then, for guaranteeing the durability of wheel-support rolling bearing unit 1a, be provided with outer cover 16a in the axial inboard of described combined seal ring 17.This outer cover 16a passes through bending and forming metallic sheets, thereby section is roughly crank shape, and integral body constitutes circular.This outer cover 16a is by being embedded in the axial inner ends portion of described wheel hub 3 (inner ring 8) to tighten chimeric mode outward with its inside diameter, thereby under the state of the axial inboard of the described combined seal ring 17 of whole covering, is fixed on the wheel hub 3.In addition, by with the outer circumferential face of the outer diameter part of outer cover 16a and described outer ring 2 near opposed, thereby between outer cover 16a and outer ring 2, form labyrinth seal.By this structure, can prevent that water droplet etc. from along with the swirling eddy that the live axle CVJ that does not show among the figure produces, directly impacting combined seal ring 17.
On the other hand, seal the seal ring 14a of axial outer end side opening of described inner space 15 shown in Fig. 2 (a), formed by arbor 30 and sealing material body 31.Arbor 30 with bending and forming metallic sheets such as Mild Sheet Steels after and form, it has: chimeric tube portion 34; Round wheel part 35, its thus the axial outer end edge of chimeric tube portion 34 to the radial outside bending; And bending part 36, its thus chimeric tube portion 34 the axial inner ends edge to radially inner side and axially the outside turn back take the shape of the letter U after, again to the radially inner side bending.And, on the embedded outer end inner peripheral surface that is fixed on described outer ring 2 of the chimeric tube portion 34 of tightening that chimeric mode will be wherein, and through under the state of a part of sealing material body 31, the axial inner side surface of round wheel part 35 is withstood on the axial outer end face of outer ring 2.
Described sealing material body 31 is to be made by the elastomer elastomeric material of rubber like, and its joint is fixed on the arbor 30, possesses three contact seal lip 32a, 32b, 32c, and the eaves shape labyrinth seal lip 33 that constitutes labyrinth seal.Each sealing lip 32a～32c makes the top edge inner side surface of sliding contact rotation side flange 12 or the intermediate portion outer circumferential face of wheel hub 3 on complete cycle respectively separately.In addition, as the elastic material of sealing material body 31, can use NBR (nitrile butadiene rubber), acrylic rubber, fluorine rubber, silicone rubber etc.
Described labyrinth seal lip 33 is compared with the described sealing lip 32a that is arranged on by radial outside, is arranged on more by radial outside, and makes its tip portion extend to the axial outside of the sliding contact point of sealing lip 32a.And then because the relation of the stepped part 37 on the axial outer end portion outer circumferential face of described outer ring 2 and the inner side surface that is arranged on described rotation side flange 12, the formation position of labyrinth seal lip 33 is restricted.In addition, described stepped part 37 is for guaranteeing to connect with respect to the flexural rigidity that is applied to the torque load on the rotation side flange 12 part of heavy section 38 and thinner wall section 39, described heavy section 38 is arranged on the part (root) of the close cardinal extremity of this rotation side flange 12, described thinner wall section 39 is arranged on the part on the close top of rotation side flange 12, and wall thickness is less than this heavy section 38.
Described labyrinth seal lip 33 (tip portion to base end part) is compared with the outside dimension of the axial outer end portion outer circumferential face of described outer ring 2 and is positioned at radial outside, and compare with described stepped part 37 and to be positioned at radial outside, and make the first half of labyrinth seal lip 33 and stepped part 37 overlapping diametrically.And, the outer circumferential face that makes the tip portion inner peripheral surface of labyrinth seal lip 33 and stepped part 37 on complete cycle near opposed.So just, can between the inner side surface of the top edge of labyrinth seal lip 33 and described rotation side flange 12, form labyrinth seal radially, and between the outer circumferential face of the tip portion inner peripheral surface of labyrinth seal lip 33 and stepped part 37, form axial labyrinth seal.
The inner peripheral surface of labyrinth seal lip 33 and outer circumferential face are partial circle conical surface shape, this partial circle conical surface shape becomes big direction and tilts along diameter dimension towards top edge, so just, the foreign matters such as muddy water that enter the internal side diameter of labyrinth seal lip 33 easily can be discharged, and the muddy water etc. that will be attached to the outer circumferential face top of labyrinth seal lip 33 guides to the direction away from tip portion.
In addition, the described labyrinth seal lip 33 that constitutes labyrinth seal contact with rotation side flange 12, therefore be attached on the labyrinth seal lip 33 after the mixing of lubricating grease and mud for preventing, and oiling agent such as uncoated lubricating grease.And then, if the surface of labyrinth seal lip 33 is adopted bright side (even surface) or adopted the face of having implemented the outstanding trickle convex-concave processing of drainage performance, then can guide muddy water into downside rapidly, prevent that further mud etc. is attached on the labyrinth seal lip 33.
For reducing running torque and keeping sealing, the lubricating grease that described sealing lip 32a～32c coating is used for lubricating that must be beyond labyrinth seal lip 33, but the lubricating grease of coating should be filled in described inner space 15 in the grease composition that is used for lubricating identical (kind of base oil and water-thickening agent is identical).Even if the lubricating grease that is coated on like this on sealing lip 32a～32c mixes with the lubricating grease that is filled in inner space 15, also can avoid greasy property deterioration to occur.In addition, if adopt the outstanding urea class lubricating grease of water repellency, even if then leak in the labyrinth seal lip 33 also not can be attached on the labyrinth seal lip 33 after muddy water mixes, therefore can be at sealing lip 32a～32c coating urea class lubricating grease (moisture metallic soap class lubricating grease and not preferred easily).
In addition, constitute the outside dimension of round wheel part 35 of described arbor 30 greater than the outside dimension of the axial outer end portion outer circumferential face of outer ring 2, and be provided with the outer periphery of the axial outer end portion of outer ring 2 and compare more to the outstanding dyke 41 of radial outside.The outer circumferential face that can stop the moisture 2 arrival labyrinth seal lips 33 along the outer ring on the outer circumferential face that is attached to outer ring 2 by this dyke 41.
And then described sealing material body 31 covers the axial inner side surface of round wheel part 35 from the base end part of labyrinth seal lip 33, and is provided with prominent bar 40 at the complete cycle of the axial inner side surface part of the round wheel part 35 that contacts with the axial outer end face of described outer ring 2.So just, can prevent foreign matters such as muddy water from the outer ring 2 and the chimeric surface of seal ring 14a enter inner space 15.2 when being pressed into chimeric seal ring 14a in the outer ring, because labyrinth seal lip 33 is compared with the outer diametric plane of outer ring 2 and is arranged on radial outside, therefore can guarantee fully that the face that is pressed into (face that 2 axial outer end face is pressed to the outer ring) is the round wheel part 35 of arbor 30, thus indentation sealing circle 14a easily.
Wheel-support rolling bearing unit of the present utility model according to such formation, can under the situation that does not increase rotational resistance, improve the sealability of seal ring, further improve preventing that foreign matter from entering the effect that rotor arranges the space, and have IMAGE.
Especially in recent years the knuckle (not shown) that constitutes draft hitch has realized lightweight, in the part of upwards clamping in week (recess of flange among Fig. 1 (b) (2 points, 6 points, 10 positions)), between the inner peripheral surface of the outer circumferential face of outer ring 2 and knuckle, there is the slit by each mounting hole 18,18 of described Stationary side flange 5 sometimes.In this structure, foreign matters such as muddy water can easily arrive the outer circumferential face of outer ring 2 by described slit, therefore the seal arrangement that seals the end of inner space 15 can be exposed in the abominable muddy water environment, but if promoted the wheel-support rolling bearing unit 1a of the present utility model of the sealability of seal arrangement, then can be fit to use.
In addition, the wheel-support rolling bearing unit of present embodiment is not limited to illustrate form, can carry out various distortion.
In the wheel-support rolling bearing unit, when turn inside diameter etc., relative tilt can take place in Internal and external cycle, described labyrinth seal lip 33 might contact with described rotation side flange 12, though therefore the inside of labyrinth seal lip 33 does not arrange arbor, if but with the external diameter end of arbor 30 to axial inside bend (with reference to figure 3 (b)) strengthening dyke 41, just can prevent effectively that 2 outer circumferential face enters sealing from the outer ring.
In addition, be the R shape with larger diameter size to the section of the influential stepped part 37 of intensity of rotation side flange 12, therefore its outside diameter end can be near the head of double-screw bolt 13 sometimes.At this moment, if the tip portion position of labyrinth seal lip 33 is too near double-screw bolt 13, influence with regard to the swirling eddy rolled because of double-screw bolt 13 heads easily deforms, the therefore thickening of preferably labyrinth seal lip 33 being carried out to a certain degree, and be arranged on position away from double-screw bolt 13.
[the 2nd mode of execution]
Fig. 3 has shown the 2nd mode of execution of the present utility model.In the present embodiment, become big for preventing the wheel-support rolling bearing unit volume, and guarantee bigger torque rigidity, adopted the different structure of two row rotor pitch diameters (PCD) (hereinafter referred to as reducing PCD structure).The hub body 7b that constitutes the wheel hub 3a of wheel-support rolling bearing unit 1b has the 1st inner race track 10a at axial intermediate portion, and is embedded with inner ring 8 outside axial inner ends portion, and described inner ring 8 has the 2nd inner race track 10b at outer circumferential face.And, after the radial outside plastic deformation, form pressurization part 20 by the inner end that makes hub body 7b, can be with inner ring 8 in conjunction with being fixed on the hub body 7b.And then, among described the 1st inner race track 10a, the 2nd inner race track 10b, the diameter of the 1st inner race track 10a in the axial outside is made as diameter greater than the 2nd axially inboard inner race track 10b.On the other hand, outer ring 2a is formed with the 1st outer race track 6a and the 2nd outer race track 6b respectively on the side face within it, among described two outer race track 6a, the 6b, the diameter of the outer race track 6a in the axial outside is made as diameter greater than axially inboard outer race track 6b.
And, between the 1st outer race track 6a and the 1st inner race track 10a, be provided with a plurality of rotor 4a in the mode of freely rotating, between the 2nd outer race track 6b and the 2nd inner race track 10b, be provided with a plurality of rotor 4b in the mode of freely rotating.Described each rotor 4a, 4b that is configured to multiple row carried out precompressed, and give its back side combined wrapping angle.And the pitch diameter of described two row rotor 4a, 4b is according to the diameter difference of the 1st inner race track 10a, the 2nd inner race track 10b and the 1st outer race track 6a, the 2nd outer race track 6b and different.That is, the pitch diameter of the rotor 4a of the row (outer rows) in the axial outside is greater than the pitch diameter of the rotor 4b of axially inboard row (inner column).
Among the different wheel-support rolling bearing unit 1b of each pitch diameter of two row each rotor 4a, 4b, the amount that can should be able to increase the pitch diameter of outer rows mutually increases torque rigidity, thus riding stability and durability when improving turning driving.In addition, owing to need not to increase the pitch diameter of inner column, need not to increase diameter so constitute the mounting hole (not shown) of the knuckle of draft hitch, therefore can make the knuckle miniaturization and.In addition, be made as diameter less than the rotor 4b of inner column by the diameter with the rotor 4a of outer rows, the quantity of the rotor 4a of outer rows is made as quantity more than the rotor 4b of inner column, thereby can further improve the rigidity of wheel-support rolling bearing unit 1b.In addition, though among the figure in the example, described each rotor 4a, 4b have used ball, support when using hub at heavy weight wheels of automobile, also can use for example circular cone roller bearing sometimes.
Among the wheel-support rolling bearing unit 1b that this pitch diameter with outer rows increases, will inevitably increase the outside dimension of outer ring 2a, the radial gap that is arranged between the outer circumferential face of the head of the double-screw bolt 13 of rotation on the side flange 12 and outer ring 2a can diminish, therefore be difficult in the radially overlapping state of the stepped part 37 of rotating side flange 12 under the labyrinth seal lip is set.Therefore, shown in Fig. 3 (b), the radially overlapping labyrinth seal lip 33a of stepped part 43 on the axial inner side surface with the heavy section 38 that is formed at rotation side flange 12 is set, with the outer circumferential face of the tip portion inner peripheral surface of this labyrinth seal lip 33a and stepped part 43 on complete cycle near opposed.So just, can between the inner side surface of the top edge of labyrinth seal lip 33a and rotation side flange 12, form labyrinth seal radially, and between the outer circumferential face of the tip portion inner peripheral surface of labyrinth seal lip 33a and stepped part 43, form axial labyrinth seal.
Described labyrinth seal lip 33a is arranged on the position with the axial outer end portion inner peripheral surface axial overlap of outer ring 2a, so just, can fully guarantee seal ring 14b is pressed into and be entrenched in the be pressed into face round wheel part 35 of outer ring 2a when going up, therefore seal ring 14b easily can be pressed into outer ring 2.
In addition, also can replace described stepped part 43, form annular recess at the heavy section 38 of rotation side flange 12, and the tip portion that makes the labyrinth seal lip therewith the inside of annular recess near opposed.In addition, the plane that the axial inner side surface of heavy section 38 of rotation side flange 12 can adopt Round Wheel, and can with the tip portion of labyrinth seal lip in the axial direction therewith the plane near opposed.
And then, in the present embodiment, be provided with dyke 41a by the sealing material body 31 that constitutes described seal ring 14b.By using sealing material body 31 to cover in the round wheel part 35 that constitutes arbor 30a to compare with the outer circumferential face of outer ring 2a to the outstanding part of radial outside and by the external side brim of round wheel part 35 cylindrical part 42 to axial inboard bending, constitute this dyke 41a.Be made as outside dimension greater than the outer circumferential face of the axial outer end portion of outer ring 2a by the internal diameter size with dyke 41a, can form that inner peripheral surface three bread by the axial inner side surface of the outer circumferential face of the axial outer end portion of outer ring 2a, dyke 41a and dyke 41a enclose at the complete cycle of outer ring 2a and axially in the groove of side opening.
Yet, for fully guaranteeing the durability of above-mentioned wheel-support rolling bearing unit 1b, must consider to be present in the scope of described two outer race track 6a, 6b heat treatment hardened layer partly.As shown in Figure 3, inner peripheral surface form two outer race track 6a, 6b outer ring 2a radial thickness axially outer half one and axial in half one differ greatly.Particularly, the wall thickness of the outer race track 6a of the outer rows that pitch diameter is bigger is less than the wall thickness of the outer race track 6b of the less inner column of pitch diameter.Be the performance optimum performance, must suitably stipulate to be present in the heat treatment hardened layer of two outer race track 6a, 6b part.
In the present embodiment, as shown in Figure 4, in the axial part of the inner peripheral surface of outer ring 2a, forming heat treatment hardened layer 70a, 70b (with the part of oblique grid representation) at the complete cycle of the part that comprises multiple row outer race track 6a, 6b respectively by high frequency hardening.
Described two heat treatment hardened layer 70a, 70b handle by separate high frequency heat and form.And, heat treatment hardened layer 70a, the 70b of two outer race track 6a, 6b have stipulated its scope, make no matter being applied to torque load on the wheel-support rolling bearing unit 1b and thrust load has muchly, be present in contacting ellipse and can not exceed two heat treatment hardened layer 70a, 70b on the rolling contact section of the rotation surface of each rotor 4a, 4b and two outer race track 6a, 6b.In addition, between two heat treatment hardened layer 70a, the 70b of the inner peripheral surface of outer ring 2a, exist non-sclerosis part 71 in the part that is formed with the planar groove shoulder 73 of non-cylinder curved face part 72 that shape of generatrix is circular arc and cylinder.Therefore described heat treatment hardened layer 70a, 70b are separated from each other by this non-sclerosis part 71.And then, the thickness of the heat treatment hardened layer 70a of the outer race track 6a of outer rows part is made as thickness greater than the heat treatment hardened layer 70b of the outer race track 6b part of inner column.
In addition, when wheel-support rolling bearing unit 1b was applied bigger thrust load etc., the wrapping angle that can make inboard outer race track 6b and rotor 4b became big as shown in Fig. 4 dot and dash line β.At this moment, stipulated the radius of curvature of described non-cylinder curved face part 72, made that the load line of action of dot and dash line β direction unanimity can not exceed outside the 2a of outer ring at the internal side diameter of the outer circumferential face of outer ring 2a therewith.The rigidity of support that so just can prevent the rotor 4b of inner column reduces or produces excessive stress in the part of outer ring 2a.
Fig. 5 has shown the variation of the 2nd mode of execution of the present utility model.In the present embodiment, on the axial intermediate portion inner peripheral surface of outer ring 2b, the section shape (shape of generatrix) of the intermediate portion of two outer race track 6a, 6b (Fig. 5 conus portions 74 of corresponding diagram 4 non-cylinder curved face part 72) is straight line.Therefore, being shaped as along internal diameter of this conus portion 74 becomes the partial circle taper concave surface that big direction tilts towards the axial outside.
In addition, in the part except the axial two end part of the inner peripheral surface of outer ring 2b, by high frequency hardening respectively the complete cycle in multiple row outer race track 6a, 6b and intermediate portion forming heat treatment hardened layer 70a, 70b, 70c (with the part of oblique grid representation).Described each heat treatment hardened layer 70a, 70b, 70c handle by high frequency heat and form, this high frequency heat is handled and is used the one-piece type high frequency heating coil with outer circumferential face shape identical with the inner peripheral surface of outer ring 2b, and two outer race track 6a, 6b and intermediate portion are heated simultaneously.In addition, described each heat treatment hardened layer 70a, 70b, 70c are mutually continuous one-piece type, and except each thickness difference, other character are identical.In addition, consider the rolling fatigue life of guaranteeing two outer race track 6a, 6b and the aspect of print resistance, stipulated the thickness of heat treatment hardened layer 70a, 70b, general car is about 2～4mm during with wheel-support rolling bearing unit, is preferably about 2～3mm.
With respect to this, be present on the heat treatment hardened layer 70c non-sclerosis part 71 on every side, can follow the heat treatment generation of heat treatment hardened layer 70c towards the stress of radially inner side, and this stress can transmit to heat treatment hardened layer 70a, the 70b of two outer race track 6a, 6b part, consider the aspect that as far as possible increases this stress, stipulated the thickness of heat treatment hardened layer 70c of the intermediate portion of two outer race track 6a, 6b, general car is about 1～3mm during with wheel-support rolling bearing unit, is preferably about 1～2mm.The thickness of heat treatment hardened layer 70c is controlled to be at least, and this heat treatment hardened layer 70c does not reach the degree as the radial outside of the imaginary cone tube face of bus with the common tangent line α of the section shape of two outer race track 6a, 6b.
The structure of other parts and effect are identical with above-mentioned the 1st mode of execution, so same section use same-sign, and the repetitive description thereof will be omitted.
[the 3rd mode of execution]
Fig. 6,7 has shown the 3rd mode of execution of the present utility model.Present embodiment is identical with above-mentioned the 2nd mode of execution, adopts the different reducing PCD structure of two row rotor pitch diameters, but seal ring 14c, combined seal ring 17a and different to the structure existence of rotation side flange 12 installation wheels.
Seal ring 14c in the present embodiment is shown in Fig. 7 (a), and the outer circumferential face of labyrinth seal lip 33b adopts the cylinder link to each other with dyke 41a planar, and its outside dimension is made as outside dimension greater than the outer circumferential face of the axial outer end portion of outer ring 2a.And, labyrinth seal lip 33b compares with the stepped part 37 of rotation side flange 12 and is positioned at radial outside, and under the radially overlapping state of the first half that makes labyrinth seal lip 33b and stepped part 37, with the outer circumferential face of the tip portion inner peripheral surface of labyrinth seal lip 33b and stepped part 37 on complete cycle near opposed, thereby form labyrinth seal.
In addition, be assembled in combined seal ring 17a among the wheel-support rolling bearing unit 1c of present embodiment shown in Fig. 7 (b), complete cycle at the axial inner side surface of the rotation side round wheel part 53 that constitutes flinger ring 50 is equipped with encoder 59, this encoder 59 branch sperromagnetism powder and integral body in macromolecular materials such as rubber, synthetic resin are Round Wheel, and are made by permanent magnet.This encoder 59 forms the tip side periphery (outer periphery) that covers rotation side round wheel part 53, and and a part of inner peripheral surface of elastic material 55 between constitute labyrinth seal 61, this elastic material 55 is covered with the inner peripheral surface of the Stationary side cylindrical part 57 of the arbor 54 that constitutes seal ring 51a.And then, in the part of elastic material 55, inner peripheral surface by Stationary side cylindrical part 57 and with outside diameter half one of the axial inner side surface of the common Stationary side round wheel part 58 that constitutes arbors 54 of Stationary side cylindrical part 57, in the part that is divided into radial outside and the axial outside, be provided with and radially reach axial thickness size greater than the heavy section 62 of the thickness size of other parts.In the elastic material 55, being the outside diameter curved surface 65 (bight R) of quadrant arcuation by section shape, is that the part of the section difference face 63 of Round Wheel and close the head portion that covers the inner peripheral surface of Stationary side cylindrical part 57 (axial interior half one) is connected smoothly with the axial inner ends face of this heavy section 62.The radius of curvature of the section shape of this external diameter N-Side surf 65 is made as radial width size greater than described labyrinth seal 61.So just make the foreign matter that enters in the space segment of the outside diameter that is present in following auxiliary seal lip 64 by labyrinth seal 61 be back to labyrinth seal 61 sides easily.
And then, extend auxiliary seal lip 64 (each sealing lip 56a～56c forms one with elastic material 55) from the radial inner end of described section poor face 63 to rotation side round wheel part 53.In addition, auxiliary seal lip 64 is to be cardinal extremity with section difference face 63, along diameter towards axial inboard tilt the gradually local circular cone tubular of extension of big direction that becomes with launching.The base end part outer circumferential face of this auxiliary seal lip 64 and section difference face 63 are that the internal side diameter curved surface 66 of quadrant arcuation is connected smoothly by section shape also.Consider that inhibition is applied to the stress of the base end part of auxiliary seal lip 64, and the aspect of easy suitably crooked this auxiliary seal lip 64, and then consider to make easily by labyrinth seal 61 and enter the aspect that foreign matter in the space segment of the outside diameter that is present in auxiliary seal lip 64 is back to these labyrinth seal 61 sides, suitably stipulated the radius of curvature of the section shape of this internal side diameter curved surface 66.Therefore, the radius of curvature of the section shape of internal side diameter curved surface 66 is made as identical or bigger with the thickness of the base end part of auxiliary seal lip 64.
The effect of this auxiliary seal lip 64 is to reduce foreign matter to be attached to the internal side diameter that is present in this auxiliary seal lip 64 and to be called as on the sealing lip 56a of close space outerpace of lateral lip, and does not require to have high leak tightness.The more important thing is and prevent from becoming big because the rotational resistance (braking torque) that auxiliary seal lip 64 causes assembling the wheel-support rolling bearing unit 1c of combined seal ring 17a is set.Therefore, in the present embodiment, suppress slip resistance by following method and increase because auxiliary seal lip 64 is set.
The wedge-like that the section shape of auxiliary seal lip 64 adopts thickness size to diminish towards top edge.So just, can reduce the elasticity of the tip portion of auxiliary seal lip 64, prevent that slip resistance from becoming big.
And then, the thickness size of auxiliary seal lip 54 is made as enough thickness size less than sealing lip 56a.Particularly, the thickness size of the base end part of thick in the auxiliary seal lip 64 is made as among the sealing lip 56a below 1/2 of thickness size of the base end part of thin part, more preferably below 1/3, but considers that moldability then will be made as more than 1/5.So just, can reduce the elasticity of auxiliary seal lip 64 integral body, prevent that slip resistance from becoming big.
And then, under the state of combined seal ring 51a and flinger ring 50, the magnitude of interference of auxiliary seal lip 64 is made as enough magnitude of interference less than sealing lip 56a.Particularly, under as the described free state of Fig. 7 (b), the axial height of auxiliary seal lip 64 (towards the axial overhang of rotation side round wheel part 53) is made as enough axial height less than sealing lip 56a.Like this under the state that is making up seal ring 51a and flinger ring 50, elastic deformation amount's (axial compression amount) of auxiliary seal lip 64 can be made as enough elastic deformation amounts less than sealing lip 56a, thereby suppress the area pressure of top edge with the slide part of the axial outer side surface of rotation side round wheel part 53 of auxiliary seal lip 64, prevent that slip resistance from becoming big.
In addition, because auxiliary seal lip 64 does not require to have high leak tightness, therefore under the state of central shaft along with turn inside diameter the travels run-off the straight of etc.ing of the central shaft of seal ring 51a and flinger ring 50, the top edge of auxiliary seal lip 64 can be a little from the axial outer side surface levitating (magnitude of interference is zero or vacates the gap a little) of rotation side round wheel part 53.In addition, can make the top edge of auxiliary seal lip 64 opposed through micro gap at complete cycle with the axial outer side surface of rotation side round wheel part 53.
No matter which kind of situation exists under the state of auxiliary seal lip 64 between sealing lip 56a and labyrinth seal 61, and the part that is communicated with labyrinth seal 61 in the space outerpace side of auxiliary seal lip 64 is provided with outer side space 60.Radially inside and outside two peripheral portions that constitute the section difference face 63 in this outer side space 60 pass through described outside diameter curved surface 65 and internal side diameter curved surface 66 respectively, are connected smoothly with radially inside and outside two side faces in outer side space 60.And then the outer circumferential face of the auxiliary seal lip 64 that is connected by internal side diameter curved surface 66 is along the direction near labyrinth seal 61 tilts towards the top.By this structure, can change foreign matter thus labyrinth seal 61 be blown into the flow direction in the outer side space 60 suddenly, and reflux to this labyrinth seal 61.
Wheel-support rolling bearing unit 1c according to the present embodiment of the combined seal ring 17a that is making up said structure, between flinger ring 50 and seal ring 51a, can effectively prevent the sealed inner that foreign matters such as muddy water enter the bearing private side that is present in sealing lip 56a.Especially can prevent that foreign matter is attached to is present among each sealing lip 56a～56c near the outer circumferential face of the sealing lip 56a in the part of labyrinth seal 61, avoids the action of this sealing lip 56a to be affected, and can prevent that reducing appears in the sealability of sealing lip 56a here.That is, section difference face 63 and auxiliary seal lip 64 by labyrinth seal 61, the axial outer end face of separating outer side space 60 and inner peripheral surface suppress foreign matter and enter in the space of the internal side diameter that is present in auxiliary seal lip 64.
Different with the respective embodiments described above, on the described rotation side flange 12 in the present embodiment, replace double-screw bolt to be provided with a plurality of screw holes 21 that forming internal thread at inner peripheral surface.When being fixed on the wheel (not shown) that constitutes wheel on the rotation side flange 12, under the fixing state with the penetration hole alignment with each screw hole 21 and wheel, fixed-use bolt is inserted from the wheel side, screw togather with screw hole 21, and further fastening.In this structure, the head of double-screw bolt is not present in the axial inner side surface that rotates side flange 12, and therefore the restriction of the radial position of the labyrinth seal lip 33b of described seal ring 14c obtains relaxing, and can use labyrinth seal lip 33b better.
In the present embodiment, in the axial intermediate portion outer circumferential face of hub body 7b, the heavy section 38 that slides from sealing lip as shown in Figure 8, is formed with heat treatment hardened layer 75 with continuum of states on the complete cycle on the part of the chimeric path stepped part 26 that inner ring 8 fixedly arranged.In addition, this heat treatment hardened layer 75 is continuous in the axial inner ends part that is present in path stepped part 26 parts incessantly from the axial outer end part that is present in heavy section 38 parts.This heat treatment hardened layer 75 by high frequency heating coil to necessity part (needing to form the part of this heat treatment hardened layer 75) heating after, carry out chilling by spraying freezing mixture etc. again and form.The shape of the high frequency heating coil that uses should match with described necessary partial shape.
Be formed with in the axial intermediate portion outer circumferential face of hub body 7b of above-mentioned heat treatment hardened layer 75, to implement to be intended to make the abrasive machining of surface smoothing to the part of path stepped part 26 from the heavy section 38 in the axial outside.This abrasive machining as shown in Figure 9, using forming grinding wheel is that revolving wheel 80 carries out.The part that forms heat treatment hardened layer 75 on the axial intermediate portion outer circumferential face of the outer circumferential face shape of this revolving wheel 80 and hub body 7b match (shape of generatrix basically identical).Carry out abrasive machining by such use revolving wheel 80, part (slip surface that comprises sealing lip) and the chimeric surface of inner ring 8 that will be formed with heat treatment hardened layer 75 are processed into even surface.
On the other hand, in the axial intermediate portion inner peripheral surface of outer ring 2a, two row outer race track 6a, 6b and be present on the part in the middle of the inner peripheral surface between described two outer race track 6a, the 6b as shown in figure 10, are formed with heat treatment hardened layer 76 with continuum of states on the complete cycle.In addition, this heat treatment hardened layer 76 is continuous incessantly at the intermediate portion of two outer race track 6a, 6b and described two outer race track 6a, 6b.This heat treatment hardened layer 76 by high frequency heating coil to necessity part (needing to form the part of this heat treatment hardened layer 76) heating after, carry out chilling by spraying freezing mixture etc. again and form.
Be formed with in the axial intermediate portion inner peripheral surface of outer ring 2a of above-mentioned heat treatment hardened layer 76, two row outer race track 6a, 6b implemented to be intended to make the abrasive machining of surface smoothing.This abrasive machining as shown in figure 11, using forming grinding wheel is that revolving wheel 81 carries out.The part that forms heat treatment hardened layer 76 on the axial intermediate portion inner peripheral surface of the outer circumferential face shape of this revolving wheel 81 and outer ring 2a match (shape of generatrix basically identical).Carry out abrasive machining by such use revolving wheel 81, will be formed with the part of heat treatment hardened layer 76 and the face that is pressed into of seal ring and be processed into even surface.
Figure 12 has shown the variation of the outer ring abrasive machining in the present embodiment.The grinding instrument that uses for two outer race track 6a, 6b are carried out abrasive machining is in the mode concentric with running shaft 82, will form the 1st circular emery wheel 83 and the 2nd emery wheel 84 respectively and go up in conjunction with the intermediate portion that is fixed on running shaft 82 and tip portion (right part of Figure 12) and form.The radius of curvature of the shape of generatrix of the outer circumferential face of the 1st emery wheel 83 is made as with the radius of curvature of the shape of generatrix of outer race track 6a and equates.In addition, the radius of curvature of the shape of generatrix of the outer circumferential face of the 2nd emery wheel 84 is made as with the radius of curvature of the shape of generatrix of outer race track 6b and equates.In addition, the outside dimension of the 1st emery wheel 83 is made as outside dimension greater than the 2nd emery wheel 84, and the external diameter difference of described the 1st emery wheel 83 and the 2nd emery wheel 84 is made as with the diameter difference of two outer race track 6a, 6b equates in fact.And then, shown in following Figure 12 (C), stipulated the axially spacing between last the 1st emery wheel 83 and the 2nd emery wheel 84, made that the 1st emery wheel 83, the 2nd emery wheel 84 are aimed at simultaneously and to be contacted two outer race track 6a, 6b under the state of the central axes of the central shaft of running shaft 82 and outer ring 2a.
Use this grinding with instrument to two outer race track 6a, when 6b carries out abrasive machining, at first shown in Figure 12 (A), under the central shaft that makes running shaft 82 state consistent with the central shaft of outer ring 2a, grind with the tip portion of instrument this opposed with the opening portion near the outer ring 2a of bigger outer race track 6a one side of diameter dimension.Shown in Figure 12 (A) → (B), advance towards outer ring 2a vertically with instrument by making grinding then, make the 1st emery wheel 83, the 2nd emery wheel 84 enter the radially inner side of outer ring 2a by the opening portion near outer race track 6a one side.And, under the state that so enters, make the phase place of the phase place of axially last two outer race track 6a, 6b and the 1st emery wheel 83, the 2nd emery wheel 84 consistent with each other.Shown in Figure 12 (B) → (C), make grinding with radially displacement of instrument by the inboard at outer ring 2a then, the 1st emery wheel 83 is pressed on the outer race track 6a, and the 2nd emery wheel 84 is pressed on the outer race track 6b.And, under this state, rotate with instrument is relative with grinding by making outer ring 2a, on complete cycle, two outer race track 6a, 6b are carried out abrasive machining.
Yet, in this variation, if be made as the proterties (granularity, conjugation, tissue) of the 1st emery wheel 83, the 2nd emery wheel 84 equal, then the trend that the trend of generation grains of sand obstruction or the generation grains of sand overflow on each working surface of the 1st emery wheel 83, the 2nd emery wheel 84 can differ greatly, and therefore may be difficult to impose a condition and grind two outer race track 6a, 6b simultaneously.Therefore, for preventing this problem, preferably by the relation according to the diameter difference between the diameter difference between two outer race track 6a, the 6b and the 1st emery wheel 83, the 2nd emery wheel 84, make in the granularity, conjugation, tissue of the 1st emery wheel 83, the 2nd emery wheel 84 at least one proterties different, be made as basic identical with the trend that the grains of sand overflow taking place on each working surface of the 1st emery wheel 83, the 2nd emery wheel 84 or the trend that the grains of sand stop up taking place.
Figure 13 has shown other variation of outer ring abrasive machining in the present embodiment.In this variation, be made as equal with constituting grinding with the outside dimension of the 1st emery wheel 83a of instrument and the outside dimension of the 2nd emery wheel 84a.In addition, shown in following Figure 13 (C), stipulated the spacing between axial last the 1st emery wheel 83a and the 2nd emery wheel 84a, made under the state of central shaft with respect to the inclined of outer ring 2a of running shaft 82 that the 1st emery wheel 83a, the 2nd emery wheel 84a aim at contact two outer race track 6a, 6b simultaneously.
Use this grinding with instrument to two outer race track 6a, when 6b carries out abrasive machining, at first shown in Figure 13 (A), (part that contacts with each working surface of the 1st emery wheel 83a, the 2nd emery wheel 84a during abrasive machining in two outer race track 6a, 6b marks common tangent line Y with respect to the state of the inclined of outer ring 2a at the central shaft that makes running shaft 82, make the central shaft X state parallel with this common tangent line Y of running shaft 82) under, the opening portion of the outer ring 2a of the outer race track 6a that tip portion and the close diameter dimension of this grinding usefulness instrument is bigger is opposed.
Then shown in Figure 13 (A) → (B), grind with instrument along axially the advancing towards outer ring 2a of this outer ring 2a by making, make the 1st emery wheel 83a, the 2nd emery wheel 84a enter the radially inner side of outer ring 2a by the opening portion of close outer race track 6a one side.And, under the state that so enters, make the phase place of the phase place of axial last two outer race track 6a, 6b of outer ring 2a and the 1st emery wheel 83a, the 2nd emery wheel 84a consistent with each other.Shown in Figure 13 (B) → (C), make grinding with the radial displacement of instrument along this outer ring 2a by the inboard at outer ring 2a then, the 1st emery wheel 83a is pressed on the outer race track 6a, and the 2nd emery wheel 84a is pressed on the outer race track 6b.In addition, when so the 2nd emery wheel 84a being pressed into outer race track 6b and going up, in order not allow the shoulder of ora terminalis part and outer race track 6b of this 2nd emery wheel 84a clash, be formed with escape groove 85 at the complete cycle of the ora terminalis part of the working surface of the 2nd emery wheel 84a.Thereafter grinding operation step and structure, effect and the effect of other parts are identical during with above-mentioned the 3rd mode of execution variation.In addition, in the structure of this example, the also trend that each working surface generation grains of sand of the 1st emery wheel 83a, the 2nd emery wheel 84a are overflowed or the trend that the grains of sand stop up takes place be made as basic identical.
The structure of other parts and effect are identical with above-mentioned the 2nd mode of execution, so same section use same-sign, and the repetitive description thereof will be omitted.
[the 4th mode of execution]
Figure 14 has shown the 4th mode of execution of the present utility model.The wheel-support rolling bearing unit 1d of present embodiment is identical with above-mentioned the 2nd, 3 mode of executions, adopts the different reducing PCD of two row rotor pitch diameters structure, but as driving wheel with having adopted and the integrated structure of constant velocity joint (CVJ).
Central part at hub body 7c is provided with splined hole 19, and directly is being formed with inner race track 10b on the shell 22 of the constant velocity joint that the axial inside part of hub body 7c is combined.And with the splined shaft 23 insertion splined holes 19 of constant velocity joint, the pressurization part 20a by the axial outer end portion that makes this splined shaft 23 forms towards the radial outside plastic deformation is fixed on hub body 7c combination on the constant velocity joint.
In the present embodiment, by having the seal ring 14d of labyrinth seal lip 33, the axial outer end opening sealing of the inner space 15 of rotor 4a, 4b will be provided with.Wheel takes up muddy water through regular meeting during driving wheel, and peripheral parts such as brake do not adopt cylinder yet, and adopts disc rotor, so wheel-support rolling bearing unit 1d is exposed in the external environment condition through regular meeting.Therefore, be fit to use by possessing the seal ring 14d that labyrinth seal lip 33 improves sealability.When being the front-wheel of the FF car of deflecting roller and 4WD car in particular for driving wheel, be more preferably.
The structure of other parts and effect are identical with above-mentioned the 3rd mode of execution, so same section use same-sign, and the repetitive description thereof will be omitted.
[the 5th mode of execution]
Figure 15 has shown the 5th mode of execution of the present utility model.The driving wheel of present embodiment is studied with the shape of the pressurization part 20b of wheel-support rolling bearing unit 1e, to prevent that the pressurization part 20b that inner ring 8 is pressed on the hub body 7a because of thrust load plastic deformation is taken place, described thrust load is to produce when the nut 9a that fastening and male screw sections splined shaft 23 tip portion screw togather.Particularly, be processed as the pressurizing mold of tabular surface or cut processing etc. in the laggard driving of pressurization processing by use, with inner ring 8 in conjunction with the axial inner ends face that is fixed on the pressurization part 20b of hub body 7a axial inner ends portion, forming perpendicular to wheel hub 3 central shafts and be the tabular surface 24 of Round Wheel.
The tabular surface 24 of this Round Wheel so that at least a portion of this tabular surface 24 (near outer peripheral portion) compare the state that is positioned at radial outside with the inner peripheral surface of inner ring 8 and form, and make the axial inner ends face of tabular surface 24 and inner ring 8 overlapping in the axial direction.And, with the live axle of wheel hub 3 and constant velocity joint be splined shaft 23 in conjunction with the time, the axial outer end face that is formed on the shoulder 25 on the shell 22a of constant velocity joint is withstood on the tabular surface 24 of pressurization part 20b.And, under this state, by tightening the nut 9a that screws togather with the male screw thread that is formed on splined shaft 23 tip portion, between nut 9a and shoulder 25, clamp wheel hub 7a.
Among the wheel-support rolling bearing unit 1e of present embodiment, under the state with wheel hub 7a and splined shaft 23 combinations, the axial outer end face of the tabular surface 24 of pressurization part 20b and the shoulder 25 of shell 22a carries out face at complete cycle and contacts.Therefore, can reduce area pressure on the axial inner ends face that fastening force by nut 9a is applied to pressurization part 20b.
In the present embodiment, by having the seal ring 14e of labyrinth seal lip, the axial outer end opening sealing of the inner space 15 of rotor 4 will be provided with.Wheel takes up muddy water through regular meeting during driving wheel, and wheel-support rolling bearing unit 1e is exposed in the external environment condition through regular meeting.Therefore, be fit to use by possessing the seal ring 14e that the labyrinth seal lip improves sealability.
The structure of other parts and effect are identical with above-mentioned the 1st mode of execution, so same section use same-sign, and the repetitive description thereof will be omitted.
[the 6th mode of execution]
Figure 16 has shown the 6th mode of execution of the present utility model.Present embodiment is the wheel-support rolling bearing unit 1f of follower (front-wheel of FR car, RR car, MR car, the trailing wheel of FF car) usefulness, therefore hub body 7 is solid body, seal ring 14f between axial outer end portion inner peripheral surface by being arranged on outer ring 2 and the axial intermediate portion outer circumferential face of hub body 7 can seal the axial outer end opening portion of the inner space 15 that is provided with rotor 4.With respect to this, the outer cover 16 by as shown in FIG. or be arranged on the axial inner ends portion inner peripheral surface of outer ring 2 and the axial inner ends portion outer circumferential face of inner ring 8 between combined seal ring, can the axial inner ends opening portion of inner space 15 be sealed.
For preventing that fully foreign matter from entering in the inner space 15, and prevent that fully the lubricating grease that are filled in this inner space 15 from leaking, fully the both ends open portion of sealed inner 15.Especially guide the foreign matter of radially inner side into and enter in the inner space 15 along the foreign matter that the outer circumferential face of outer ring 2 is guided the axial outer end opening portion of outer ring 2 into along the inner side surface of rotation side flange 12 for preventing, the seal ring 14f that requires to be used for the axial outer end opening portion of this inner space 15 of sealing has outstanding sealability.During follower, be under the situation of front-wheel of FR car, RR car, MR car of deflecting roller at follower, the part that constitutes braking device is disc rotor, and wheel-support rolling bearing unit 1f can be exposed in the external environment condition, therefore the preferred seal ring 14f with labyrinth seal lip and dyke that uses.
Present embodiment is identical with described the 3rd mode of execution, by have and the stepped part 37 of axial inner peripheral surface of rotation side flange 12 between form the seal ring 14f of the labyrinth seal lip 33b of labyrinth seal, can suppress foreign matter and enter in the labyrinth seal along the axial inner peripheral surface of rotation side flange 12.In addition, owing to be provided with outside dimension greater than the dyke 41a of the axial outer end portion outer circumferential face of outer ring 2, therefore can stop moisture on the outer circumferential face that is attached to outer ring 2 to arrive the outer circumferential face of labyrinth seal lip 33 along the outer circumferential face of this outer ring 2.
Yet, in the axial outer end portion of the wheel hub 3 that constitutes wheel-support rolling bearing unit 1f, when being provided with the disc rotor that will not show among the figure and wheel and being installed on the wheel hub 3 as the guide portion 27 of centrally aligned standard.This guide portion 27 and rotation side flange 12 are compared further outstanding and constitute the general cylindrical shape shape to the axial outside, and described disc rotor and wheel are entrenched on its outer circumferential face.In the present embodiment, for antirust (preventing that disc rotor and wheel from getting rusty) etc., implemented cathode electro-coating and formed coated film 90 at outer circumferential face, axial inner ends face and the aperture surface of this guide portion 27.
The formation of the cathode electro-coating film that uses in the following simple declaration present embodiment.For after the grease of removing wheel hub 3 carries out cleaning by degreasing etc., carry out drying again.Installing electrodes on this dried wheel hub 3, only all faces and the aperture surface with guide portion 27 is immersed in the plating tank that dissociable water-soluble fluidity coating is housed, and arrange between the electrode in the plating tank and apply voltage, will through being ionized into for cationic coating ion plating on the side face and aperture surface of guide portion 27.In order clearly to distinguish the application part, in electroplanting device, by pump coating is circulated in plating tank, and the spill-out of plating tank is made as fixed value, thereby guarantee fixing application scope.So just, can reduce by coating liquid fluctuating or device and rock the influence that brings.After coated film was electroplated and finished, high-temperature baking and cooling again made the sclerosis of electro dipping film, thereby finishes coated film 90.
The coated film 90 that produces like this can be formed uniformly thinner coated film, and damage, peel off etc. dangerous less, rust-proof effect is good.In addition, coated film 90 also can be by toasting to make to the coating after brushing application or the spary application.And then, can also form coated film 90 by the anion electroplating application of using negative ion (anion) coating or the electrostatic spraying that charged vaporific coating (ion microparticle) is attached on the wheel hub 3.
The structure of other parts and effect are identical with above-mentioned the 3rd mode of execution, so same section use same-sign, and the repetitive description thereof will be omitted.
[the 7th mode of execution]
Figure 17 has shown the 7th mode of execution of the present utility model.Under the situation of present embodiment, for preventing that wheel-support rolling bearing unit from gaining in weight, and improve the life-span of bearing, adopt the different reducing PCD structure of two row rotor pitch diameters, but different with above-mentioned the 2nd mode of execution, it is arranged to big footpath with axial inboard row (inner column).
Constitute the hub body 7d of the wheel hub 3c of wheel-support rolling bearing unit 1g in the present embodiment by pressurization part 20b, the inner ring 8a that will have the 1st inner race track 10c and have the 2nd inner race track 10d at outer circumferential face at axial intermediate portion is in conjunction with being fixed on axial inner ends portion.And then, among described the 1st inner race track 10c, the 2nd inner race track 10d, the diameter of the 2nd inner race track 10d of axial inboard is made as greater than the axial diameter of the 1st inner race track 10c in the outside.On the other hand, outer ring 2c is formed with the 1st outer race track 6c and the 2nd outer race track 6d respectively on the side face within it, among described two outer race track 6c, the 6d, the diameter of the 2nd outer race track 6d of axial inboard is made as greater than the axial diameter of the 1st outer race track 6c in the outside.
And, between the 1st outer race track 6c and the 1st inner race track 10c, be provided with a plurality of rotor 4c in the mode of freely rotating, between the 2nd outer race track 6d and the 2nd inner race track 10d, be provided with a plurality of rotor 4d in the mode of freely rotating.Described each rotor 4c, 4d that is configured to multiple row carried out precompressed, and give its back side combined wrapping angle.And the pitch diameter of described two row rotor 4c, 4d is according to the diameter difference of the 1st inner race track 10c, the 2nd inner race track 10d and the 1st outer race track 6c, the 2nd outer race track 6d and different.That is, the pitch diameter of the rotor 4d of the row (inner column) of axial inboard is greater than the pitch diameter of the rotor 4c of the row (outer rows) in the axial outside.
In addition, in the present embodiment, by having the seal ring 14g of labyrinth seal lip 33, the axial outer end opening sealing of the inner space 15 of rotor 4c, 4d will be provided with.Seal ring 14g has the sealing lip of three contact-types, and wherein two sealing lip 32a, 32b make the sliding contact on complete cycle of each top edge rotate the inner side surface of side flange 12.
Among the wheel-support rolling bearing unit 1g of the pitch diameter of this increase inner column, by the structure that the wheel hub 3c that wheel is installed is carried out one-sided support, rotor 4d to inner column applies bigger load, but owing to improved load-carrying ability behind the pitch diameter of increase rotor 4d, the use fatigue that therefore can suppress rotor 4d, the 2nd outer race track 6d and the 2nd inner race track 10d, thereby life-saving.So basis is applied to the definite pitch diameter separately of difference of the load load on each rotor 4c, 4d, so the life-span of each rotor 4c, 4d is identical, thereby can improve the durability of wheel-support rolling bearing unit 1g.
Therefore in addition, the outside dimension in the axial outside of outer ring 2c diminishes, and the diameter dimension of labyrinth seal lip 33 also can diminish, and can reduce to be arranged on the inner side surface of rotation side flange 12 and form the diameter dimension of the stepped part 37 of labyrinth seals with labyrinth seal lip 33.Therefore, as realizing wheel-support rolling bearing unit 1g lightweight and reducing to rotate the structure of the inertia (moment of inertia) of side flange 12, can improve the rideability (riding comfort, acceleration performance etc.) of automobile.In addition, though the rotation of accompanying rotation side flange 12, the head of double-screw bolt 13 can produce swirling eddy, but because labyrinth seal lip 33 is away from the head of double-screw bolt 13, can suppress labyrinth seal lip 33 distortion that the influence because of swirling eddy causes, therefore can reduce the slit, labyrinth of labyrinth seal lip 33 and stepped part 37, improve the sealability of labyrinth seal lip 33.
Figure 18 has shown the variation of the 7th mode of execution of the present utility model.In this variation, seal ring 14h, inner ring 8b and the structure difference of wheel being installed to rotation side flange 12.On the rotation side flange 12 of this variation, identical with above-mentioned the 3rd mode of execution, replace double-screw bolt to be provided with a plurality of screw holes 21 that form female screw thread at inner peripheral surface.
Among the seal ring 14h of this variation, be entrenched in the be pressed into face round wheel part 35 of outer ring 2c when going up and compare at internal side diameter and be provided with labyrinth seal lip 33a with seal ring 14h is pressed into, seal ring 14h easily can be pressed into outer ring 2c like this.In addition, by will further being arranged on internal side diameter near the formation position of the stepped part 37 of opposed rotation side flange 12 with labyrinth seal lip 33a, can realize further lightweight and the low inertiaization of wheel-support rolling bearing unit 1h.And then, the labyrinth seal of 37 of labyrinth seal lip 33a and stepped part is arranged on more near internal side diameter, the inhibition slit, labyrinth that the Internal and external cycle relative tilt of (turning action of automobile etc.) causes during because of moment load changes, and therefore can reduce the slit, labyrinth, improves the labyrinth seal effect.
In addition, by hub body 7d clamping, thickening is the side wall thickness in the outside axially under the state that its bi-side is adjacent to hub body 7d for inner ring 8b, and it is poor to reduce with the wall thickness of the side of axial inboard.Therefore the heat treatment deformation that so just can suppress inner ring 8b can cut down means of abrasion, shortens the abrasive machining time, and then because the difference in areas of the bi-side of inner ring 8b is less, so can adopt the higher two plane lapping of efficient to process, thus reduce cost.In addition, even if axially the retainer 11 of outer rows is to the bearing inboard (axially inboard) when mobile, also can the side in the axial outside of inner ring 8b not with retainer 11 position contacting on, inner ring 8b is fixed on the hub body 7d.
In addition, when the wheel-support rolling bearing unit 1h of the reducing PCD structure that axial inner column is made as big footpath as this variation is heat-treated, preferably the effective case depth of the 1st outer race track 6c in the axial outside of outer ring 2c is processed as the effective case depth less than the 2nd axially inboard outer race track 6d, overheated thereby the groove shoulder (with the part of the axial inboard adjacency of outer race track 6c) that suppresses the 1st outer race track 6c occurs.
The structure of other parts and effect are identical with above-mentioned the 2nd mode of execution, so same section use same-sign, and the repetitive description thereof will be omitted.
[the 8th mode of execution]
Figure 19 has shown the 8th mode of execution of the present utility model.Among the wheel-support rolling bearing unit 1i of present embodiment, labyrinth seal lip 33 has been carried out machining near the stepped part 37a of opposed hub body 7e.In addition, inner peripheral surface forms female screw hole 21 and is provided with a plurality of (with reference to described the 3rd mode of execution) at rotation side flange 12, and makes the dyke 41b of seal ring 14i extend to the position of screw hole 21 axial overlaps therewith to outside diameter.
The hub body 7e that constitutes wheel hub 3d uses middle-carbon steel manufacturing such as S53C to form, during manufacturing columned steel billet is heated to carry out forging molding more than the A3 transition point after, remove the patina (scale) on surface by sandblast etc.And the axial outer side surface of the rotation side flange 12 of fixation disc type impeller and wheel is processed into tabular surface by machining.In addition, as described among the hub body 7a shown in the 1st mode of execution, at the axial inner side surface of rotation side flange 12, the part of the seat surface (contacting with head) of the head that becomes double-screw bolt 13 is carried out machining.Then, after the axial intermediate portion outer circumferential face of hub body 7e forms the heat treatment hardened layer by high frequency hardening (with reference to figure 8), to be intended to make the abrasive machining (with reference to figure 9) of surface smoothing to the chimeric part enforcement that the path stepped part 26 of inner ring 8 fixedly arranged from the heavy section 38 of sealing lip 32a sliding contact.
And then in the present embodiment, on the outer circumferential face of described stepped part 37a, at least to labyrinth seal lip 33 near opposed and part that form labyrinth seal has been carried out machining at complete cycle.Therefore, compare during for forging plane with stepped part, the dimensional accuracy of stepped part 37a is improved, and its surface smoothing, therefore can reduce the slit, labyrinth, thereby improves the sealability of seal ring 14i.In addition, even if when labyrinth seal lip 33 contacts with stepped part 37a, can prevent that also 33 damages of labyrinth seal lip or running torque from increasing.
In addition, about the machining of stepped part 37a, can advance to drive a vehicle at high frequency hardening and cut processing, also can behind high frequency hardening, carry out abrasive machining to inner race track 10 and heavy section 38 etc. simultaneously.In addition, the section shape of stepped part 37a also can adopt tilted shape (conical surface) except circular shape (toroidal surface) as shown in figure 19.
Replace double-screw bolt 13 to be provided with in the structure of present embodiment of screw hole 21, owing to do not have the head of double-screw bolt, so even if labyrinth seal lip 33 near screw holes 21, also can not cause 33 distortion of labyrinth seal lip because of above-mentioned swirling eddy.In addition, because the operation when need not to consider to be double-screw bolt 13 from the part that the axial inboard replacing of rotation side flange 12 will be changed, therefore the dyke 41b by making seal ring 14i extends to position with screw hole 21 axial overlaps to outside diameter, can improve the water resistence of seal ring 14i.
The structure of other parts and effect are identical with above-mentioned the 1st mode of execution, so same section use same-sign, and the repetitive description thereof will be omitted.
Wheel-support rolling bearing unit of the present utility model is suitable as automotive wheel is supported on bearing unit on the draft hitch.

Claims (2)

1. wheel-support rolling bearing unit, it has: the outer ring has outer race track on the side face within it; Wheel hub has inner race track with the opposed part of described outer race track in its outer circumferential face, and this wheel hub and described outer ring concentric arrangement; A plurality of rotors, it is arranged between described outer race track and the described inner race track in the mode of freely rotating; Flange, it is arranged in the outer circumferential face of described wheel hub and compares outstanding laterally part with the outer end opening portion of described outer ring; And seal ring, it is used for sealing the outer end opening portion of the inner space between the outer circumferential face of the inner peripheral surface that is present in described outer ring and described wheel hub; It is characterized in that,
Described seal ring is strengthened and is constituted with the sealing material body that elastic material is made by the arbor of the outer end that is fixed on described outer ring and by arbor, this sealing material body has: at least one sealing lip, the inner side surface of its described flange of sliding contact on complete cycle or the outer circumferential face of described wheel hub; And labyrinth seal lip, its therewith sealing lip compare and be set to more close radial outside, and its tip portion is close opposed with the inner side surface of described flange on complete cycle, thereby and the inner side surface of described flange between form labyrinth seal, the lubricating grease that described inner space is filled with to lubricate, be provided with and the opposed round wheel part in the exterior edge face of described outer ring at described arbor
The external diameter edge of described round wheel part is compared to radial outside outstanding with the exterior edge face outer periphery of described outer ring, be coated with the lubricating grease identical with the grease composition of described inner space or urea class lubricating grease on the described sealing lip.
2. wheel-support rolling bearing unit as claimed in claim 1 is characterized in that, in described seal ring, uncoated lubricating grease on the described labyrinth seal lip only is coated with described lubricating grease at described sealing lip.
CN2013202397558U 2012-12-26 2013-04-25 Rolling bearing unit for wheel support Expired - Fee Related CN203189534U (en)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
JP2012282630 2012-12-26
JP2012-282630 2012-12-26
JP2013038076A JP2014142054A (en) 2012-12-26 2013-02-28 Wheel support rolling bearing unit
JP2013-038076 2013-02-28

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Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104565081A (en) * 2013-10-23 2015-04-29 株式会社捷太格特 Wheel bearing device
CN105179466A (en) * 2014-06-12 2015-12-23 Skf公司 Rolling Bearing, Particularly For Clutch Release Bearing Device
CN105508435A (en) * 2014-10-13 2016-04-20 斯凯孚公司 Bearing, clutch bearing device and motor vehicle equipped with the clutch bearing device
CN106402152A (en) * 2016-12-09 2017-02-15 瓦房店轴承集团有限责任公司 Self-aligning roller bearing for elevator sealing
CN106507636A (en) * 2015-09-04 2017-03-15 丰田自动车株式会社 Coolant channel attachment structure and cooling system
CN108700118A (en) * 2016-04-12 2018-10-23 日本精工株式会社 Hub unit bearing
EP3276196A4 (en) * 2015-03-27 2019-01-02 NSK Ltd. Vehicle wheel bearing unit
CN109312783A (en) * 2016-06-21 2019-02-05 Ntn株式会社 Rolling bearing system
CN109983261A (en) * 2016-12-16 2019-07-05 舍弗勒技术股份两合公司 Sealing device and sealing unit

Cited By (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104565081B (en) * 2013-10-23 2018-09-18 株式会社捷太格特 Bearing apparatus for wheel
CN104565081A (en) * 2013-10-23 2015-04-29 株式会社捷太格特 Wheel bearing device
CN105179466B (en) * 2014-06-12 2019-08-20 Skf公司 Rolling bearing is especially used for the rolling bearing of clutch release bearing device
CN105179466A (en) * 2014-06-12 2015-12-23 Skf公司 Rolling Bearing, Particularly For Clutch Release Bearing Device
CN105508435A (en) * 2014-10-13 2016-04-20 斯凯孚公司 Bearing, clutch bearing device and motor vehicle equipped with the clutch bearing device
EP3276196A4 (en) * 2015-03-27 2019-01-02 NSK Ltd. Vehicle wheel bearing unit
CN106507636A (en) * 2015-09-04 2017-03-15 丰田自动车株式会社 Coolant channel attachment structure and cooling system
CN106507636B (en) * 2015-09-04 2018-11-16 丰田自动车株式会社 Coolant channel connection structure and cooling system
CN108700118B (en) * 2016-04-12 2019-12-03 日本精工株式会社 Hub unit bearing
CN108700118A (en) * 2016-04-12 2018-10-23 日本精工株式会社 Hub unit bearing
CN109312783A (en) * 2016-06-21 2019-02-05 Ntn株式会社 Rolling bearing system
CN109312783B (en) * 2016-06-21 2020-08-14 Ntn株式会社 Rolling bearing device
CN106402152A (en) * 2016-12-09 2017-02-15 瓦房店轴承集团有限责任公司 Self-aligning roller bearing for elevator sealing
CN109983261A (en) * 2016-12-16 2019-07-05 舍弗勒技术股份两合公司 Sealing device and sealing unit
US11092239B2 (en) 2016-12-16 2021-08-17 Schaeffler Technologies AG & Co. KG Seal device and seal assembly

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