JP2013061048A - Bearing unit for supporting wheel with seal - Google Patents

Bearing unit for supporting wheel with seal Download PDF

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Publication number
JP2013061048A
JP2013061048A JP2011201381A JP2011201381A JP2013061048A JP 2013061048 A JP2013061048 A JP 2013061048A JP 2011201381 A JP2011201381 A JP 2011201381A JP 2011201381 A JP2011201381 A JP 2011201381A JP 2013061048 A JP2013061048 A JP 2013061048A
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Prior art keywords
seal
lip
outer ring
ring
bearing unit
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JP2011201381A
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Japanese (ja)
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Masamitsu Watabe
将充 渡部
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NSK Ltd
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NSK Ltd
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Priority to JP2011201381A priority Critical patent/JP2013061048A/en
Publication of JP2013061048A publication Critical patent/JP2013061048A/en
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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
    • 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
    • F16C19/186—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
    • F16C2326/00—Articles relating to transporting
    • F16C2326/01—Parts of vehicles in general
    • F16C2326/02—Wheel hubs or castors

Abstract

PROBLEM TO BE SOLVED: To provide a bearing unit for supporting a wheel with a seal, which maintains stable seal performance by enhancing muddy water resistance, and can easily be manufactured.SOLUTION: A seal ring 13a at the side of a rotating flange 8 comprises: a cylinder 22 press-fitted into the internal periphery of the end of an outer ring 2; a core metal 20 composed of a support plate 23 extending from the cylinder 22 toward the inside of the radial direction; and a synthetic rubber seal member having a side lip 24a and a main lip 25 which are vulcanized and adhered to the core metal, and inclined and extended to the outside of the radial direction. A recess 30 is formed at the rotating flange 8, the side lip 24a forms the labyrinth seal which does not contact with the inside surface of the recess 30, a sliding face 32 on which the main lip 25 slide-moves is formed at the inside-diameter side rather than the recess 30 of the rotating flange 8, and a boundary 31 between the recess 30 and the sliding face 32 is located inside more than the inside surface of the rotating flange 8 in the axial direction.

Description

本発明は、自動車の懸架装置に対して車輪を回転自在に支持する為の車輪支持用軸受ユニットに関し、特に、回転支持部分に組み込むシール装置の耐泥水性を高め、シールリップの摩耗を防止することにより、シール性能を向上させたシール付車輪支持用軸受ユニットに関するものである。   The present invention relates to a wheel-supporting bearing unit for rotatably supporting a wheel with respect to a suspension device of an automobile, and in particular, improves the muddy water resistance of a seal device incorporated in a rotation support portion and prevents wear of a seal lip. Thus, the present invention relates to a bearing unit for supporting a wheel with a seal whose sealing performance is improved.

従来より、自動車の車輪を懸架装置に回転自在に支持する為に車輪支持用軸受ユニットが使用されており、この車輪支持用軸受ユニットの従来例を図６に示す。図６に示す車輪支持用軸受ユニット１は、自動車の懸架装置に支持する駆動輪（ＦＦ車の前輪、ＦＲ車及びＲＲ車の後輪、４ＷＤ車の全輪）用として使用される車輪支持用軸受ユニットの１例である。静止輪であり中炭素鋼等の金属製の外輪２は、外周面に形成した外向フランジ状の取付部３により、懸架装置の構成部材であるナックル（不図示）に支持固定されて、使用時にも回転しない。   Conventionally, a wheel support bearing unit has been used to rotatably support a vehicle wheel on a suspension device. FIG. 6 shows a conventional example of this wheel support bearing unit. The wheel support bearing unit 1 shown in FIG. 6 is used for wheel support used for driving wheels (front wheels of FF vehicles, rear wheels of FR and RR vehicles, all wheels of 4WD vehicles) supported by a suspension system of an automobile. It is an example of a bearing unit. A stationary outer ring 2 made of metal such as medium carbon steel is supported and fixed to a knuckle (not shown) which is a structural member of the suspension device by an outward flange-shaped mounting portion 3 formed on the outer peripheral surface. Also does not rotate.

前記外輪２の内径側には、回転輪となるハブ４を、この外輪２と同心に設け、使用時においてこのハブ４が回転する様にしている。このハブ４は、中炭素鋼等の金属製のハブ本体５と、軸受鋼等の金属製の内輪６とから成る。このうちのハブ本体５の中心部内周面にはスプライン孔７を、軸方向外寄り（軸方向に関して、車両への組み付け時に幅方向外側になる方向を「外」と言い、各図の左側）部外周面には、外向フランジ状の回転フランジ８を、軸方向内寄り（軸方向に関して、車両への組み付け時に幅方向内側になる方向を「内」と言い、各図の右側）部外周面には、内輪６を外嵌固定する小径段部１６を、それぞれ形成している。そして、前記ハブ本体５の軸方向内端の先端部を径方向外方に塑性変形させてかしめ部１７を形成し、このかしめ部１７により、ハブ本体５と共にハブ４を構成する内輪６の内端面を抑え付けている。車両への組み付け時に前記スプライン孔７には、等速ジョイントに付属したスプライン軸（不図示）を挿入し、前記回転フランジ８には車輪（不図示）を固定する。   A hub 4 serving as a rotating wheel is provided concentrically with the outer ring 2 on the inner diameter side of the outer ring 2 so that the hub 4 rotates in use. The hub 4 includes a hub body 5 made of metal such as medium carbon steel and an inner ring 6 made of metal such as bearing steel. Of these, the spline hole 7 is formed on the inner peripheral surface of the central portion of the hub body 5 outwardly in the axial direction. On the outer peripheral surface of the part, the outward flange-shaped rotary flange 8 is inward in the axial direction (the direction that becomes the inner side in the width direction when assembled to the vehicle with respect to the axial direction is referred to as “inside”, the right side of each figure). Are formed with small-diameter step portions 16 on which the inner ring 6 is externally fitted and fixed. The tip end portion of the inner end in the axial direction of the hub main body 5 is plastically deformed radially outward to form a caulking portion 17, and the caulking portion 17 forms an inner ring 6 that constitutes the hub 4 together with the hub main body 5. The end face is held down. A spline shaft (not shown) attached to a constant velocity joint is inserted into the spline hole 7 when assembled to a vehicle, and a wheel (not shown) is fixed to the rotating flange 8.

又、前記外輪２の内周面に複列の外輪軌道９、９を、前記ハブ本体５の中間部外周面と前記内輪６の外周面とに内輪軌道１０、１０を、それぞれ形成している。そして、これら各外輪軌道９、９と内輪軌道１０、１０との間に転動体１１、１１を、それぞれ複数個ずつ設けて、外輪２の内径側でのハブ４の回転を自在としている。尚、上記各転動体１１、１１は、それぞれ保持器１２、１２により、転動自在に保持されている。又、図示の例では転動体１１、１１として玉を使用しているが、重量が嵩む車両用の軸受の場合には、転動体として円すいころを使用する事もできる。更に、ハブ本体５の中間部外周面に形成された内輪軌道１０は、このハブ本体５の中間部外周面に別体の内輪を外嵌し、この内輪の外周面に形成する事もできる。   Double row outer ring raceways 9 and 9 are formed on the inner peripheral surface of the outer ring 2, and inner ring raceways 10 and 10 are formed on the outer peripheral surface of the intermediate portion of the hub body 5 and the outer peripheral surface of the inner ring 6, respectively. . A plurality of rolling elements 11, 11 are provided between the outer ring raceways 9, 9 and the inner ring raceways 10, 10, respectively, so that the hub 4 can freely rotate on the inner diameter side of the outer ring 2. The rolling elements 11 and 11 are held by the cages 12 and 12 so as to freely roll. Further, in the illustrated example, balls are used as the rolling elements 11, 11, but in the case of a vehicle bearing that is heavy in weight, a tapered roller can be used as the rolling element. Further, the inner ring raceway 10 formed on the outer peripheral surface of the intermediate portion of the hub body 5 can be formed on the outer peripheral surface of the inner ring by fitting a separate inner ring on the outer peripheral surface of the intermediate portion of the hub main body 5.

又、前記外輪２の外端部内周面と前記ハブ本体５の中間部外周面との間にはシールリング１３を設け、外輪２の内端部内周面と前記内輪６の内端部外周面との間にパックシール１４を設ける事により、外輪２の内周面と前記ハブ４の外周面との間で、各転動体１１、１１を設置した空間の両端開口を塞いでいる。尚、図示の例の場合、パックシール１４の軸方向内側面にエンコーダ１５を設け、ハブ４（すなわち車輪）の回転速度を検出可能な構造としている。このエンコーダ１５の回転速度を検出する為のセンサ（不図示）は、懸架装置を構成するナックル等に設置する。   A seal ring 13 is provided between the inner peripheral surface of the outer end of the outer ring 2 and the outer peripheral surface of the intermediate portion of the hub body 5, and the inner peripheral surface of the inner end of the outer ring 2 and the outer peripheral surface of the inner end of the inner ring 6. By providing the pack seal 14 therebetween, the opening at both ends of the space where the rolling elements 11 and 11 are installed is closed between the inner peripheral surface of the outer ring 2 and the outer peripheral surface of the hub 4. In the case of the illustrated example, an encoder 15 is provided on the inner surface in the axial direction of the pack seal 14 so that the rotational speed of the hub 4 (ie, the wheel) can be detected. A sensor (not shown) for detecting the rotation speed of the encoder 15 is installed in a knuckle or the like constituting the suspension device.

そして、車輪支持用軸受ユニット１の軸方向内端開口部を塞ぐパックシール１４は、ゴム等のエラストマーにより造られた３本のシールリップを備え、各シールリップは、断面略Ｌ字形で全体を円環状に成形されて外輪２に内嵌固定された芯金にその基端部を結合固定している。そして、これら各シールリップの先端縁を、断面Ｌ字形で全体を円環状に成形されて内輪６に外嵌固定されたスリンガに、それぞれ摺動させている。   The pack seal 14 that closes the axially inner end opening of the wheel support bearing unit 1 includes three seal lips made of an elastomer such as rubber, and each seal lip is substantially L-shaped in cross section. The base end portion is coupled and fixed to a metal core that is formed in an annular shape and is fitted and fixed to the outer ring 2. The leading edges of these seal lips are respectively slid on slingers that are L-shaped in cross-section and are formed into an annular shape and are fitted and fixed to the inner ring 6.

一方、各転動体１１、１１を設置した空間の軸方向外端開口部を密封するシールリング１３は、図７に示す様に構成している。このシールリング１３は、それぞれが円環状に形成された芯金２０と弾性材２１とから成る。このうちの芯金２０は、軟鋼板等の金属板にプレス加工等の打ち抜き加工並びに塑性加工を施す事により、一体成形しており、前記外輪２の軸方向外端部内周面に内嵌固定自在な円筒部２２と、この円筒部２２の外端縁から直径方向内方に折れ曲がった支持板部２３とを備える。そして、この円筒部２２は、外輪２の軸方向外端開口部に、締まり嵌めで内嵌固定されている。
前記芯金２０と共にシールリング１３を構成する弾性材２１は、ゴム等のエラストマーにより造り、芯金２０に対し、モールド成形、加硫接着等により接合固定している。この様な弾性材２１は、支持板部２３の軸方向外側面を、全周に亙り完全に覆っており、その外側面及び内周縁に、それぞれサイドリップ２４、メインリップ２５、グリースリップ２６を形成している。そして、サイドリップ２４及びメインリップ２５を前記ハブ本体５の回転フランジ８の基端部内側面に、グリースリップ２６をこのハブ本体５の中間部外周面に、それぞれ全周に亙り摺動させている。 On the other hand, the seal ring 13 that seals the axially outer end opening of the space in which the rolling elements 11 and 11 are installed is configured as shown in FIG. The seal ring 13 includes a cored bar 20 and an elastic material 21 each formed in an annular shape. Of these, the core 20 is integrally formed by punching and plasticizing a metal plate such as a mild steel plate, and is fitted and fixed to the inner peripheral surface of the outer end of the outer ring 2 in the axial direction. A free cylindrical portion 22 and a support plate portion 23 bent inward in the diameter direction from the outer end edge of the cylindrical portion 22 are provided. The cylindrical portion 22 is internally fitted and fixed to the axially outer end opening of the outer ring 2 by an interference fit.
The elastic member 21 constituting the seal ring 13 together with the cored bar 20 is made of an elastomer such as rubber, and is bonded and fixed to the cored bar 20 by molding, vulcanization adhesion, or the like. Such an elastic material 21 completely covers the outer circumferential surface of the support plate portion 23 over the entire circumference, and a side lip 24, a main lip 25, and a grease lip 26 are provided on the outer surface and the inner circumferential edge, respectively. Forming. The side lip 24 and the main lip 25 are slid over the entire inner periphery of the hub body 5 on the inner surface of the base end portion of the rotating flange 8 and the grease lip 26 on the outer peripheral surface of the intermediate portion of the hub body 5. .

上述の様に、車輪支持用軸受ユニット１の内部空間の両端開口部（或は一方の開口部）を、シール装置により塞いで、この内部空間内に封入したグリースの漏洩を防止すると共に、外部からの塵挨、水、泥水等の軸受内部への浸入を防止している。
しかしながら、こうした従来のシール装置では、サイドリップ２４と回転フランジ８の基端部内側面との摺動部には径方向外側に遮蔽物がなく、外輪２の外端面と回転フランジ８との間に流れ込んだ泥水は容易に摺動部に到達するため、長期の使用において、その摺動部に泥水が付着して泥水中の砂を噛み込み、リップ摩耗が促進される虞がある。これにより、長期間に亘って安定したシール性能を維持できないといった問題があった。 As described above, both end openings (or one opening) of the internal space of the wheel support bearing unit 1 are closed by the sealing device to prevent leakage of grease sealed in the internal space and This prevents dust, water, muddy water, etc. from entering the bearing.
However, in such a conventional sealing device, the sliding portion between the side lip 24 and the inner side surface of the base end portion of the rotary flange 8 has no shield on the outer side in the radial direction, and between the outer end surface of the outer ring 2 and the rotary flange 8. Since the muddy water that has flowed in easily reaches the sliding portion, the muddy water may adhere to the sliding portion and bite the sand in the muddy water in a long-term use, which may promote lip wear. Thereby, there existed a problem that the stable sealing performance could not be maintained over a long period of time.

この部分の改善の先行技術として、特許文献１に記載されたシールリングを図８に示す。これによれば、外輪２とハブ４との間に形成される環状空間の開口部に装着されたシールリング１３が、外輪２の端部内周に圧入された円筒部２２、およびこの円筒部２２から径方向内方に延びる支持板部２３からなる芯金２０と、この芯金２０に加硫接着され、径方向外方に傾斜して延びるサイドリップ２４を有する合成ゴム製の弾性材２１とを備え、サイドリップ２４が摺動する相手部材に段付き部１８が形成され、この段付き部１８がサイドリップ２４の先端部を覆うように径方向外方に配置されているので、泥水等が流れ込んでもサイドリップの摺動部に滞留することなく下方に流出して排出され、この摺動部に泥水が付着してリップ摩耗が促進されることはなく、シールの耐泥水性を高め、長期間に亘ってシール性能を維持できるシール付車輪支持用軸受ユニットが開示されている。   As a prior art for improving this portion, a seal ring described in Patent Document 1 is shown in FIG. According to this, the cylindrical portion 22 in which the seal ring 13 attached to the opening of the annular space formed between the outer ring 2 and the hub 4 is press-fitted into the inner periphery of the end of the outer ring 2, and the cylindrical portion 22. An elastic material 21 made of synthetic rubber having a core metal 20 comprising a support plate portion 23 extending radially inward from the core, and a side lip 24 vulcanized and bonded to the core metal 20 and extending obliquely outward in the radial direction; The stepped portion 18 is formed in the mating member on which the side lip 24 slides, and the stepped portion 18 is disposed radially outward so as to cover the tip end portion of the side lip 24. Even if it flows in, it flows out downward without staying in the sliding part of the side lip, and muddy water adheres to this sliding part and lip wear is not promoted, improving the muddy water resistance of the seal, Seal performance can be maintained over a long period of time Lumpur wheeled supporting bearing unit is disclosed.

特開２０１１−０８９５５８号公報JP 2011-089558 A

上述の様な車輪支持用軸受ユニット１のハブ本体５は、中高炭素鋼のビレットを熱間鍛造により成形後、旋削加工する事で所望の形状としている。さらに、ハブ本体５の外周面（回転フランジ８の基端部内側面から、内輪軌道１０を含み、小径段部１６に亙る部分）は、高周波焼き入れ等の熱処理により硬化させた後、研削加工する事で、所望の性状（寸法及び表面粗さ）に仕上げている。図９は、この様な、軸受の軌道面等を研削加工により仕上げる方法に関する従来例である。ハブ本体５の外周面で、シール摺動面である回転フランジ８の基端部分から軸方向外側の内輪軌道１０を含む中間部分に掛けての部分は、ダイヤモンドホイールで成形された回転砥石１９により同時研削加工される。
上記回転砥石１９は直径４５５〜６１０ｍｍ程度の円板形状であり、研削加工時に於いて、軸方向に凹む段付き部１８の縁部と回転砥石１９の軸方向外側の縁部とが干渉し、内輪軌道面１０及び小径段部１６を同時研削可能な加工条件（例えば、回転砥石１９の接触角度３０〜４０°等）では、回転フランジ８の軸方向に加工可能な深さ、言い換えれば、回転フランジ８の内側面から軸方向外側への砥石の挿入可能な深さは僅か（０．５mm以下）である。このため、段付き部１８はもちろん、段付き部１８の内径側であり、回転フランジ８の内側面から軸方向外側に位置するシール摺動面となる部分を研削加工することは出来ない。 The hub body 5 of the wheel supporting bearing unit 1 as described above is formed into a desired shape by turning a billet of medium and high carbon steel by hot forging and then turning. Further, the outer peripheral surface of the hub body 5 (the portion including the inner ring raceway 10 and extending to the small diameter step portion 16 from the inner end surface of the rotating flange 8) is hardened by heat treatment such as induction hardening and then ground. In this way, it is finished to the desired properties (size and surface roughness). FIG. 9 shows a conventional example relating to a method of finishing the raceway surface of the bearing and the like by grinding. A portion of the outer peripheral surface of the hub main body 5 that extends from the base end portion of the rotary flange 8 that is a seal sliding surface to an intermediate portion including the inner ring raceway 10 on the outer side in the axial direction is formed by a rotating grindstone 19 formed of a diamond wheel. Simultaneous grinding.
The rotating grindstone 19 has a disk shape with a diameter of about 455 to 610 mm, and the edge of the stepped portion 18 that is recessed in the axial direction interferes with the edge on the axially outer side of the rotating grindstone 19 during grinding. Under processing conditions (for example, a contact angle of 30 to 40 degrees of the rotating grindstone 19) that allows the inner ring raceway surface 10 and the small-diameter stepped portion 16 to be ground simultaneously, the depth that can be processed in the axial direction of the rotating flange 8, in other words, rotation The depth at which the grindstone can be inserted from the inner surface of the flange 8 to the outer side in the axial direction is small (0.5 mm or less). For this reason, not only the stepped portion 18 but also the inner diameter side of the stepped portion 18 and the portion that becomes the seal sliding surface located on the outer side in the axial direction from the inner surface of the rotary flange 8 cannot be ground.

図８に示すような、各シールリップ（サイドリップ２４、メインリップ２５、グリースリップ２６）の摺動面を内輪軌道１０の溝肩から段付き部１８の近傍まで滑らかに連続した円弧形状に加工する場合、この部分は旋削加工等の機械加工により仕上げ加工を施す必要がある。しかし、シール摺動面を旋削加工等の送り目を有する加工面とすることは、シール性能の低下（送り目の谷部分からの漏洩、シール摩耗）となり好ましくない。また、シール摺動面となる回転フランジ８の基端部は、回転フランジ８に加わる回転モーメント等の外部荷重に耐える為に熱処理硬化されており、ハードターニングによる切削加工となるので、切削工具の寿命が短く粗さの管理もしにくい。また、総型バイトを用いた送り目のない機械加工は、ハードターニングの上、シール摺動面の加工範囲も広いので、実施困難である。   As shown in FIG. 8, the sliding surface of each seal lip (side lip 24, main lip 25, grease lip 26) is processed into a smoothly continuous arc shape from the groove shoulder of the inner ring raceway 10 to the vicinity of the stepped portion 18. In this case, this part needs to be finished by machining such as turning. However, it is not preferable to make the seal sliding surface a processed surface having a feed such as turning, because the sealing performance is deteriorated (leakage from the valley portion of the feed and seal wear). In addition, the base end portion of the rotary flange 8 serving as the seal sliding surface is heat-treated and hardened to withstand an external load such as a rotational moment applied to the rotary flange 8 and is cut by hard turning. Life is short and roughness is difficult to control. Further, seamless machining using a total-type tool is difficult to implement because the machining range of the seal sliding surface is wide on hard turning.

本発明は、上述の様な問題に鑑み、シール装置のリップ摩耗を防止することにより、耐泥水性を高めて安定したシール性能を維持すると共に、容易に製造できるシール付車輪支持用軸受ユニットを提供することを目的とする。   In view of the above-described problems, the present invention provides a wheel support bearing unit with a seal that can be easily manufactured while improving the muddy water resistance and maintaining a stable sealing performance by preventing lip wear of the sealing device. The purpose is to provide.

上記問題を解決するために、本発明のシール付車輪支持用軸受ユニットは、内周に複列の外輪軌道面が一体に形成された外輪と、一端部に車輪を取り付けるための回転フランジを備え、外周に複列の内輪軌道面が形成されたハブ輪と、このハブ輪と前記外輪の両軌道面に保持器を介して転動自在に収容された複数の転動体と、前記外輪とハブ輪との間に形成される環状空間の両端開口部に装着されたシール装置とを備え、前記回転フランジ側のシール装置が、前記外輪の端部内周に圧入された円筒部、およびこの円筒部から径方向内方に延びる支持板部からなる芯金と、この芯金に加硫接着され、径方向外方に傾斜して延びるサイドリップ及メインリップを有する合成ゴム製のシール部材とを備える。   In order to solve the above problem, a bearing unit for supporting a wheel with a seal according to the present invention includes an outer ring in which a double row outer ring raceway surface is integrally formed on an inner periphery, and a rotating flange for attaching a wheel to one end. A hub ring having a double row inner ring raceway surface formed on the outer periphery, a plurality of rolling elements housed on both raceway surfaces of the hub ring and the outer ring via a cage, the outer ring and the hub A cylindrical device in which the sealing device on the rotating flange side is press-fitted into the inner periphery of the end of the outer ring, and the cylindrical portion. And a synthetic rubber seal member having a side lip and a main lip that are vulcanized and bonded to the metal core and extend obliquely outward in the radial direction. .

特に、請求項１に記載したシール付車輪支持用軸受ユニットに於いては、前記回転フランジに凹部が形成され、前記サイドリップがこの凹部の内側面と非接触のラビリンスシールを形成し、前記回転フランジの前記凹部よりも内径側に前記メインリップが摺動する摺動面を形成し、前記凹部と前記摺動面との境界部が前記回転フランジの軸方向内側面より内側に配置されている。
更に、請求項２に記載したシール付車輪支持用軸受ユニットは、前記凹部が旋削加工により形成され、前記摺動面が研削加工されている。 In particular, in the bearing unit for supporting a wheel with a seal according to claim 1, a concave portion is formed in the rotating flange, and the side lip forms a non-contact labyrinth seal with an inner surface of the concave portion, and the rotation A sliding surface on which the main lip slides is formed on the inner diameter side of the concave portion of the flange, and a boundary portion between the concave portion and the sliding surface is disposed on the inner side of the axial inner surface of the rotating flange. .
Furthermore, in the bearing unit for supporting a wheel with a seal described in claim 2, the concave portion is formed by turning, and the sliding surface is ground.

本発明によれば、凹部がサイドリップの先端部を覆うように配置されており、泥水等が流れ込んでもサイドリップの先端部に滞留することがないので、この先端部に泥水が付着してリップ摩耗が促進されることはなく、シールの耐泥水性を高め、長期間に亘って安定したシール性能を維持できると共に、上記凹部が旋削加工により形成されており、加工が容易なシール付車輪支持用軸受ユニットを提供することができるという効果が有る。   According to the present invention, the concave portion is arranged so as to cover the front end portion of the side lip, and even if muddy water or the like flows, it does not stay at the front end portion of the side lip. Wear is not promoted, the muddy water resistance of the seal is increased, stable sealing performance can be maintained over a long period of time, and the recessed portion is formed by turning, and the wheel support with a seal is easy to process. There is an effect that a bearing unit can be provided.

本発明の実施の形態の第１例を示す部分断面図。The fragmentary sectional view which shows the 1st example of embodiment of this invention. 本発明の実施の形態の第２例を示す部分断面図。The fragmentary sectional view which shows the 2nd example of embodiment of this invention. 本発明の実施の形態の第３例を示す部分断面図。The fragmentary sectional view which shows the 3rd example of embodiment of this invention. 本発明の実施の形態の第４例を示す部分断面図。The fragmentary sectional view which shows the 4th example of embodiment of this invention. 本発明の実施の形態の第５例を示す部分断面図。The fragmentary sectional view which shows the 5th example of embodiment of this invention. 車輪支持用軸受ユニットの従来構造の例を示す断面図。Sectional drawing which shows the example of the conventional structure of the bearing unit for wheel support. 従来構造のシール装置の例を示す部分断面図。The fragmentary sectional view which shows the example of the sealing device of conventional structure. 従来構造のシール装置の別の例を示す部分断面図。The fragmentary sectional view which shows another example of the sealing device of conventional structure. 従来構造のハブ本体の製造工程を示す研削加工の説明図。Explanatory drawing of the grinding process which shows the manufacturing process of the hub main body of a conventional structure.

［実施の形態の第１例］
図１は、本発明の実施の形態の第１例を示している。尚、本発明の特徴は、車輪支持用軸受ユニットを構成する外輪の端部を密封するシール装置において、シールリングのサイドリップと回転フランジに設けた凹部とによりラビリンスシールを形成する部分の構造にある。外輪に対して内輪（ハブ）を回転自在に支持して成る、車輪支持用軸受ユニットの構造及び作用は、基本的には前述の図６〜９に示した従来構造と同様であるので、同等部分には同一符号を付して、重複する説明を省略若しくは簡略にし、以下、本発明の特徴部分並びに前述した従来構造と異なる部分を中心に説明する。 [First example of embodiment]
FIG. 1 shows a first example of an embodiment of the present invention. The feature of the present invention is the structure of the part that forms the labyrinth seal by the side lip of the seal ring and the recess provided in the rotating flange in the seal device that seals the end of the outer ring constituting the wheel support bearing unit. is there. Since the structure and operation of the wheel support bearing unit that rotatably supports the inner ring (hub) with respect to the outer ring are basically the same as those of the conventional structure shown in FIGS. The same reference numerals are given to the portions, and overlapping descriptions are omitted or simplified. Hereinafter, the features of the present invention and portions different from the above-described conventional structure will be mainly described.

本発明の、シール付車輪支持用軸受ユニットは、外輪２とハブ４、および転動体１１とを備え、外輪２の内径側に設けられたハブ４は、転動体１１を介して外輪２と同心に回転自在に支持されている。そして、外輪２の両端部にはシールリング１３ａ及びパックシール１４が装着され、外輪２とハブ４との間に形成される環状空間の開口部を密封している。これにより、軸受内部に封入された潤滑グリースの外部への漏洩と、外部から雨水やダスト等が軸受内部に侵入するのを防止している。このうちの、外輪２の軸方向内端側を密封するパックシール１４は、互いに対向配置されたスリンガと環状のシール板とで構成されている。   The sealed wheel support bearing unit of the present invention includes an outer ring 2, a hub 4, and a rolling element 11, and the hub 4 provided on the inner diameter side of the outer ring 2 is concentric with the outer ring 2 via the rolling element 11. Is supported rotatably. A seal ring 13 a and a pack seal 14 are attached to both ends of the outer ring 2 to seal the opening of an annular space formed between the outer ring 2 and the hub 4. This prevents leakage of the lubricating grease sealed inside the bearing and prevents rainwater, dust, etc. from entering the bearing from the outside. Of these, the pack seal 14 that seals the inner end side in the axial direction of the outer ring 2 is composed of a slinger and an annular seal plate arranged to face each other.

一方、外輪２の軸方向外端側を密封するシールリング１３ａは、図１に示すように、静止輪である外輪２の軸方向外端部内周面に所定のシメシロを介して内嵌された芯金２０と、この芯金２０に接合された弾性部材２１とからなる一体型のシールで構成されている。
芯金２０は、外輪２に圧入される円筒部２２と、この円筒部２２から径方向内方に折曲して形成される支持板部２３とからなり、全体として円環状に形成され、軟鋼板等の金属板からプレス加工にて成形されている。 On the other hand, as shown in FIG. 1, the seal ring 13a that seals the outer end side in the axial direction of the outer ring 2 is fitted into the inner peripheral surface of the outer end 2 in the axial direction of the outer ring 2 that is a stationary ring through a predetermined shimoshiro. It is composed of an integral seal composed of a core metal 20 and an elastic member 21 joined to the core metal 20.
The metal core 20 includes a cylindrical portion 22 press-fitted into the outer ring 2 and a support plate portion 23 formed by bending the cylindrical portion 22 inward in the radial direction, and is formed in an annular shape as a whole. It is formed by pressing from a metal plate such as a plate.

弾性部材２１はＮＢＲ（アクリロニトリル−ブタジエンゴム）等の合成ゴム材からなり、加硫接着によって芯金２０に一体に接合されている。この弾性部材２１は、芯金２０の円筒部２２から支持板部２３に亙って軸受外方側（軸方向外側）の表面を覆うように接合され、支持板部２３から径方向外方に傾斜して延びるサイドリップ２４ａと、このサイドリップ２４ａの内径側に径方向外方に傾斜して延びるメインリップ２５と、軸受内方側に傾斜して延びるグリースリップ２６と、を一体に有している   The elastic member 21 is made of a synthetic rubber material such as NBR (acrylonitrile-butadiene rubber) and is integrally joined to the cored bar 20 by vulcanization adhesion. The elastic member 21 is joined so as to cover the surface on the bearing outer side (axially outer side) from the cylindrical portion 22 of the metal core 20 to the support plate portion 23, and radially outward from the support plate portion 23. A side lip 24a extending in an inclined manner, a main lip 25 extending in a radially outward direction on the inner diameter side of the side lip 24a, and a grease lip 26 extending in an inclined direction toward the inner side of the bearing are integrally provided. ing

回転フランジ８の軸方向内側の基端部は研削加工により断面が円弧状の曲面に形成され、この基端部にメインリップ２５が所定の軸方向シメシロをもって全周に亙り摺動すると共に、ハブ本体５の中間部外周面（研削加工面）にグリースリップ２６が所定の径方向シメシロをもって全周に亙り摺動している。また、メインリップが摺動する摺動面３２の径方向外側で、サイドリップ２４ａが対向する回転フランジ８の基端部には、旋削加工により断面がコの字形状の凹部３０が形成されている。そして、この凹部３０の軸方向内側面とサイドリップ２４ａの軸方向外側面とは所定の軸方向すきまを介して対向し、ラビリンスシールを形成していると共に、この凹部３０の径方向内周面とサイドリップ２４ａの径方向外周面とは所定の径方向すきまを介して対向し、ラビリンスシールを形成している。さらに、この凹部３０のラビリンスシールを形成している軸方向内側面は、軸受中心軸と垂直となる円環状の平面であり、その軸方向の深さは、サイドリップ２４ａの先端部の軸方向寸法よりも大きく設定されている。   A base end portion on the inner side in the axial direction of the rotary flange 8 is formed into a curved surface having an arc shape in cross section by grinding, and a main lip 25 slides over the entire periphery with a predetermined axial direction squeezing and a hub. A grease lip 26 slides over the entire circumference with a predetermined radial direction squeezing on the outer peripheral surface (grinding surface) of the intermediate portion of the main body 5. Further, a concave portion 30 having a U-shaped cross section is formed by turning at the proximal end portion of the rotating flange 8 facing the side lip 24a on the radially outer side of the sliding surface 32 on which the main lip slides. Yes. The inner side surface in the axial direction of the concave portion 30 and the outer side surface in the axial direction of the side lip 24a are opposed to each other through a predetermined axial clearance to form a labyrinth seal, and the inner peripheral surface in the radial direction of the concave portion 30 And the radially outer peripheral surface of the side lip 24a are opposed to each other through a predetermined radial clearance to form a labyrinth seal. Further, the inner side surface in the axial direction forming the labyrinth seal of the concave portion 30 is an annular plane perpendicular to the bearing central axis, and the axial depth is the axial direction of the distal end portion of the side lip 24a. It is set larger than the dimension.

前記凹部３０は、ハブ本体５を熱間鍛造で成形後で熱処理前の状態において、旋削によりこのハブ本体５の形状を加工する時に成形される。従って、凹部３０を成形するための製造工程を新たに追加する必要はなく、熱処理硬化していない状態で旋削加工するので、凹部３０は容易に加工できる。
また、研削加工によりハブ本体５の外周面の仕上げ加工を行う場合、回転砥石１９の端部は砥粒の脱落を起しやすい（所謂小端高の発生）ので、凹部３０の旋削面とメインリップ２５が摺動する研削面（摺動面３２）との境界部３１は、回転フランジ８の軸方向内側面より内側に配置している。これにより、回転砥石１９の端部が境界部３１から離れるので、砥粒の脱落を防止すると共に、たとえ砥粒が脱落しても摺動面３２に影響することを回避することができる。なお、上記境界部３１の配置に伴い、メインリップ２５の摺動位置も回転フランジ８の軸方向内側面よりも内側としている。
なお、シールリング１３ａを外輪２に嵌合する場合、芯金２０の円筒部２２の軸方向外端部を圧入冶具で押すことにより、円筒部２２が外輪２の内周面に圧入固定されるので、サイドリップ２４の外径寸法は、円筒部２２の外径寸法より小径としている。 The recess 30 is formed when the shape of the hub body 5 is processed by turning in a state after the hub body 5 is formed by hot forging and before heat treatment. Therefore, it is not necessary to newly add a manufacturing process for forming the recess 30 and the turning 30 can be easily processed because the turning process is performed without being heat-cured.
Further, when the outer peripheral surface of the hub body 5 is finished by grinding, the end of the rotating grindstone 19 is likely to drop off abrasive grains (so-called small end height is generated). The boundary portion 31 with the grinding surface (sliding surface 32) on which the lip 25 slides is disposed on the inner side of the inner side surface in the axial direction of the rotary flange 8. Thereby, since the edge part of the rotary grindstone 19 leaves | separates from the boundary part 31, while falling off of an abrasive grain, even if an abrasive grain falls, it can avoid affecting the sliding surface 32. With the arrangement of the boundary portion 31, the sliding position of the main lip 25 is also set on the inner side of the inner side surface in the axial direction of the rotary flange 8.
When the seal ring 13 a is fitted to the outer ring 2, the cylindrical portion 22 is press-fitted and fixed to the inner peripheral surface of the outer ring 2 by pressing the axial outer end of the cylindrical portion 22 of the core metal 20 with a press-fitting jig. Therefore, the outer diameter of the side lip 24 is smaller than the outer diameter of the cylindrical portion 22.

図１に示すように、回転フランジ８の軸方向内側面と外輪２の軸方向外端面とが僅かな軸方向すきまを介してラビリンスシールを形成すと共に、サイドリップ２４ａと凹部３０とが所定のすきまを介してラビリンスシールを形成している。さらに、凹部３０により、サイドリップ２４ａの先端部（ラビリンスシール形成部）に直接泥水等がかからないように保護しているので、泥水等がサイドリップ２４ａの先端部に滞留することなく下方に流出して排出される。したがって、シールリング１３ａの耐泥水性を高め、長期間に亘って安定したシール性能を維持できるシール付車輪支持用軸受ユニットを提供することができる。
又、凹部３０とサイドリップ２４ａとは非接触のラビリンスシールを形成しているので、凹部３０を旋削加工により成形した旋削面としても、対向するサイドリップ２４ａが摩耗してシール性能が低下することはない。 As shown in FIG. 1, the inner side surface in the axial direction of the rotary flange 8 and the outer end surface in the axial direction of the outer ring 2 form a labyrinth seal through a slight axial clearance, and the side lip 24a and the concave portion 30 have a predetermined shape. A labyrinth seal is formed through the gap. Further, since the concave portion 30 protects the tip portion (labyrinth seal forming portion) of the side lip 24a from being directly exposed to muddy water or the like, the muddy water or the like flows downward without staying at the tip portion of the side lip 24a. Discharged. Accordingly, it is possible to provide a wheel support bearing unit with a seal that can increase the mud water resistance of the seal ring 13a and can maintain a stable sealing performance over a long period of time.
Further, since the concave portion 30 and the side lip 24a form a non-contact labyrinth seal, even when the concave surface 30 is formed by turning, the facing side lip 24a is worn and the sealing performance is deteriorated. There is no.

ところで、車輪支持用軸受ユニットは、モーメント荷重を負荷する軸受であり、荷重負荷時の外内輪の相対傾きは、軸受中心近傍を中心とする回転運動となることが知られている。本例の場合、凹部３０とサイドリップ２４ａとの間で軸方向及び径方向のラビリンスシールを構成しているので、例えば、径方向のラビリンスすきまが増加するような変位が起きた時には、軸方向のラビリンスすきまは減少するような関係となるので、外内輪の相対傾きが発生してもラビリンスシールの性能を保つことができる。
なお、凹部３０の内径面にサイドリップ２４ａが接触するとリップが変形してシール性能が低下するので、ラビリンスシールのすきまは、「径方向すきま＞軸方向すきま」としておくことが望ましい。また、凹部３０の表面粗さを良好にしておけばサイドリップ２４ａが凹部３０の内面と一時的に接触しても問題はないので、軸方向のラビリンスすきまはゼロとしてもよい。 By the way, it is known that the wheel support bearing unit is a bearing that applies a moment load, and the relative inclination of the outer and inner rings when the load is applied is a rotational motion centered around the center of the bearing. In this example, since the labyrinth seals in the axial direction and the radial direction are configured between the recess 30 and the side lip 24a, for example, when a displacement that increases the labyrinth clearance in the radial direction occurs, Since the labyrinth clearance is reduced, the performance of the labyrinth seal can be maintained even when the relative inclination of the outer and inner rings occurs.
Note that when the side lip 24a comes into contact with the inner diameter surface of the recess 30, the lip is deformed and the sealing performance is deteriorated. Therefore, it is desirable that the clearance of the labyrinth seal is “radial clearance> axial clearance”. Further, if the surface roughness of the recess 30 is good, there is no problem even if the side lip 24a temporarily contacts the inner surface of the recess 30, so that the labyrinth clearance in the axial direction may be zero.

［実施の形態の第２例］
図２は、本発明の実施の形態の第２例を示している。なお、この実施形態は、前述した実施の形態の第１例（図１）と基本的には同様であり、サイドリップの構造が異なるだけで、その他前述した実施形態と重複する図示には同じ符号を付してその詳細な説明を省略する。
本実施例では、サイドリップ２４ｂの先端部に、軸受中心軸に対して略垂直となる円環状の面を有する円環板部２７を設け、この円環板部２７の軸方向外面と凹部３０の軸方向内側面との間に所定の軸方向すきまを介してラビリンスシールを形成している。円環板部２７により、ラビリンスシールの径方向の距離を長くしているので、シール性能を向上することができる。 [Second Example of Embodiment]
FIG. 2 shows a second example of the embodiment of the present invention. In addition, this embodiment is basically the same as the first example (FIG. 1) of the above-described embodiment, except that the structure of the side lip is different, and is the same in the drawings that overlap with the above-described embodiment. Reference numerals are assigned and detailed description thereof is omitted.
In the present embodiment, an annular plate portion 27 having an annular surface that is substantially perpendicular to the bearing center axis is provided at the tip of the side lip 24b, and the axially outer surface of the annular plate portion 27 and the recess 30 are provided. A labyrinth seal is formed through a predetermined axial clearance between the inner surface and the inner surface in the axial direction. Since the radial distance of the labyrinth seal is increased by the annular plate portion 27, the sealing performance can be improved.

［実施の形態の第３例］
図３は、本発明の実施の形態の第３例を示している。なお、この実施形態は、前述した実施形態と基本的には同様であり、サイドリップの構造及び凹部の形状が異なるだけで、その他前述した実施形態と重複する図示には同じ符号を付してその詳細な説明を省略する。
本実施例では、旋削面である凹部３０ｃの断面を円弧形状とし、研削面である摺動面３２の円弧曲面を外径方向に延長した線よりも、軸方向外側に凹部３０ｃを形成している。
前述した様に、車輪支持用軸受ユニットは、モーメント荷重を負荷する軸受であり、回転フランジ８の基端部は、このモーメント荷重による曲げ応力が集中する位置でもある。本実施例の構成により、凹部３０ｃの形成に伴う回転フランジ８の基端部における肉厚の減少を最小限に留め、凹部３０ｃと摺動面３２とが境界部３１で滑らかに交わるようにしている。これにより、凹部３１ｃへの応力の集中を防ぐことができると伴に、高周波熱処理時に境界部３１のオーバーヒート及びそれに伴う、組織の粗粒化を防ぐことが出来るので、回転フランジ８の強度の低下を抑制する事ができる。
なお、サイドリップ２４ｃの円環板部２７ｃは、凹部３０ｃの旋削円弧面と対向する様に円弧形状として、ラビリンスシール性能を高めている。 [Third example of embodiment]
FIG. 3 shows a third example of the embodiment of the present invention. This embodiment is basically the same as the above-described embodiment, except that the structure of the side lip and the shape of the recess are different, and the same reference numerals are given to the drawings that overlap with the above-described embodiment. Detailed description thereof is omitted.
In the present embodiment, the recess 30c, which is a turning surface, has an arc shape in cross section, and the recess 30c is formed on the outer side in the axial direction from a line obtained by extending the arc curved surface of the sliding surface 32, which is a grinding surface, in the outer diameter direction. Yes.
As described above, the wheel support bearing unit is a bearing for applying a moment load, and the base end portion of the rotary flange 8 is also a position where bending stress due to the moment load is concentrated. With the configuration of the present embodiment, the reduction in the thickness at the base end portion of the rotary flange 8 due to the formation of the recess 30 c is minimized, and the recess 30 c and the sliding surface 32 smoothly cross at the boundary portion 31. Yes. Accordingly, concentration of stress in the recess 31c can be prevented, and overheating of the boundary portion 31 and accompanying grain coarsening can be prevented during high-frequency heat treatment, so that the strength of the rotating flange 8 is reduced. Can be suppressed.
The circular plate portion 27c of the side lip 24c has an arc shape so as to face the turning arc surface of the recess 30c, thereby improving the labyrinth seal performance.

［実施の形態の第４例］
図４は、本発明の実施の形態の第４例を示している。なお、この実施形態は、前述した実施形態と基本的には同様であり、サイドリップの構造及び凹部の形状が異なるだけで、その他前述した実施形態と重複する図示には同じ符号を付してその詳細な説明を省略する。
本実施例では、旋削面である凹部３０ｄを円錐面形状とし、その円錐面の断面形状は、研削面である摺動面３２の円弧曲面の境界部３１における接線と同一、或いはこの接線よりも僅かに軸方向外側に傾斜した角度を成す面としている。
これにより、凹部３０ｄの旋削加工を容易としている。他の作用効果は上記実施の形態の第３例と同様である。なお、サイドリップ２４ｄの円環板部２７ｄは、凹部３０ｄの旋削円錐面と対向する様に円錐形状としている。 [Fourth Example of Embodiment]
FIG. 4 shows a fourth example of the embodiment of the present invention. This embodiment is basically the same as the above-described embodiment, except that the structure of the side lip and the shape of the recess are different, and the same reference numerals are given to the drawings that overlap with the above-described embodiment. Detailed description thereof is omitted.
In this embodiment, the concave portion 30d which is a turning surface has a conical surface shape, and the cross-sectional shape of the conical surface is the same as or more than the tangent at the boundary 31 of the arcuate curved surface of the sliding surface 32 which is a grinding surface. It is a surface that forms an angle slightly inclined outward in the axial direction.
This facilitates turning of the recess 30d. Other functions and effects are the same as in the third example of the above embodiment. The annular plate portion 27d of the side lip 24d has a conical shape so as to face the turning conical surface of the recess 30d.

［実施の形態の第５例］
図５は、本発明の実施の形態の第５例を示している。なお、この実施形態は、前述した実施の形態の第３例と基本的には同様であり、凹部の形状が一部異なるだけで、その他前述した実施形態と重複する図示には同じ符号を付してその詳細な説明を省略する。
本実施例では、凹部３０ｅの内径面の断面形状を、軸受中心を中心とする円弧状（軸受中心を中心とする球面）としている。
これにより、外部からのモーメント荷重により軸受中心近傍を中心とした外内輪の相対回転運動が発生しても、径方向のラビリンスすきまの変化を抑制することができる。従って、サイドリップ２４ｅと凹部３０ｅとが径方向に接触する虞が無いので、径方向のラビリンスすきまを小さくして、シール性能を向上する事ができる。また、凹部３０ｅの外径寄り部分（稜部）が回転フランジ８の軸方向内側面と滑らかに交わる事により、高周波熱処理時のオーバーヒート及びそれに伴う組織の粗粒化を防ぐことが出来るので、回転フランジ８の強度の低下を招くことがない。
なお、凹部３０ｅの内径面の断面形状を、軸受中心を中心とする円弧の接線（軸受中心とを結ぶ直線が直交する円錐面）としてもよい。 [Fifth Example of Embodiment]
FIG. 5 shows a fifth example of the embodiment of the present invention. Note that this embodiment is basically the same as the third example of the above-described embodiment, except that the shape of the recess is partially different, and other illustrations that overlap with the above-described embodiment are denoted by the same reference numerals. Detailed description thereof will be omitted.
In this embodiment, the cross-sectional shape of the inner diameter surface of the recess 30e is an arc shape centered on the bearing center (a spherical surface centered on the bearing center).
Thereby, even if the relative rotational motion of the outer inner ring centered on the vicinity of the center of the bearing occurs due to the moment load from the outside, the change in the labyrinth clearance in the radial direction can be suppressed. Therefore, there is no possibility that the side lip 24e and the recess 30e contact in the radial direction, so that the radial labyrinth clearance can be reduced and the sealing performance can be improved. In addition, since the portion near the outer diameter (ridge portion) of the recess 30e smoothly intersects the axial inner side surface of the rotating flange 8, overheating during high-frequency heat treatment and accompanying coarsening of the structure can be prevented. The strength of the flange 8 is not reduced.
The cross-sectional shape of the inner diameter surface of the recess 30e may be a tangent of an arc centered on the bearing center (a conical surface in which a straight line connecting the bearing center is orthogonal).

以上、本発明の実施の形態について説明を行ったが、本発明は各実施の形態に何等限定されるものではなく、本発明の要旨を逸脱しない範囲内において、さらに種々なる形態で実施し得ることは勿論のことであり、また、前記した各実施の形態を適宜組み合わせることも可能である。   Although the embodiments of the present invention have been described above, the present invention is not limited to the embodiments and can be implemented in various forms without departing from the gist of the present invention. Of course, the above-described embodiments can be combined as appropriate.

本発明に係るシール付車輪支持用軸受ユニットは、静止輪（外輪）と回転輪（ハブ）との間に形成された環状空間の開口部にシールが装着された車輪支持用軸受ユニットに適用することができる。   The wheel support bearing unit with a seal according to the present invention is applied to a wheel support bearing unit in which a seal is attached to an opening of an annular space formed between a stationary wheel (outer ring) and a rotating wheel (hub). be able to.

１ 車輪支持用軸受ユニット
２ 外輪
３ 取付部
４ ハブ
５ ハブ本体
６ 内輪
７ スプライン孔
８ 回転フランジ
９ 外輪軌道
１０ 内輪軌道
１１ 転動体
１２ 保持器
１３、１３ａ、１３ｂ、１３ｃ、１３ｄ、１３ｅ シールリング
１４ パックシール
１５ エンコーダ
１６ 小径段部
１７ かしめ部
１８ 段付き部
１９ 回転砥石
２０ 芯金
２１ 弾性体
２２ 円筒部
２３ 支持板部
２４、２４ａ、２４ｂ、２４ｃ、２４ｄ、２４ｅ サイドリップ
２５ メインリップ
２６ グリースリップ
２７、２７ｃ、２７ｄ、２７ｅ 円環板部
３０、３０ｃ、３０ｄ、３０ｅ 凹部
３１ 境界部
３２ 摺動面 DESCRIPTION OF SYMBOLS 1 Wheel support bearing unit 2 Outer ring 3 Mounting part 4 Hub 5 Hub main body 6 Inner ring 7 Spline hole 8 Rotating flange 9 Outer ring raceway 10 Inner ring raceway 11 Rolling element 12 Cage 13, 13a, 13b, 13c, 13d, 13e Seal ring 14 Pack seal 15 Encoder 16 Small diameter step portion 17 Caulking portion 18 Stepped portion 19 Rotating whetstone 20 Core metal 21 Elastic body 22 Cylindrical portion 23 Support plate portions 24, 24a, 24b, 24c, 24d, 24e Side lip 25 Main lip 26 Grease lip 27, 27c, 27d, 27e Ring plate part 30, 30c, 30d, 30e Concave part 31 Boundary part 32 Sliding surface

Claims (2)

内周に複列の外輪軌道面が一体に形成された外輪と、一端部に車輪を取り付けるための回転フランジを備え、外周に複列の内輪軌道面が形成されたハブ輪と、このハブ輪と前記外輪の両軌道面に保持器を介して転動自在に収容された複数の転動体と、前記外輪とハブ輪との間に形成される環状空間の両端開口部に装着されたシール装置とを備え、前記回転フランジ側のシール装置が、前記外輪の端部内周に圧入された円筒部、およびこの円筒部から径方向内方に延びる支持板部からなる芯金と、この芯金に加硫接着され、径方向外方に傾斜して延びるサイドリップ及メインリップを有する合成ゴム製のシール部材とを備えたシール付車輪支持用軸受ユニットにおいて、
前記回転フランジに凹部が形成され、前記サイドリップがこの凹部の内側面と非接触のラビリンスシールを形成し、前記回転フランジの前記凹部よりも内径側に前記メインリップが摺動する摺動面を形成し、前記凹部と前記摺動面との境界部が前記回転フランジの軸方向内側面より内側に配置されている事を特徴とするシール付車輪支持用軸受ユニット。 An outer ring in which a double row outer ring raceway surface is integrally formed on the inner periphery, a hub ring having a rotation flange for attaching a wheel to one end, and a double row inner ring raceway surface on the outer periphery, and the hub ring And a plurality of rolling elements accommodated on both raceway surfaces of the outer ring via a cage, and a seal device mounted at both ends of an annular space formed between the outer ring and the hub ring A sealing device on the rotating flange side, a metal core comprising a cylindrical portion press-fitted into the inner periphery of the end of the outer ring, and a support plate extending radially inward from the cylindrical portion; In a bearing unit for supporting a wheel with a seal provided with a seal member made of a synthetic rubber having a side lip and a main lip which are vulcanized and bonded and extend obliquely outward in the radial direction,
A concave portion is formed in the rotating flange, the side lip forms a labyrinth seal that is not in contact with the inner surface of the concave portion, and a sliding surface on which the main lip slides on the inner diameter side of the concave portion of the rotating flange. A bearing unit for supporting a wheel with a seal, wherein a boundary portion between the concave portion and the sliding surface is formed on the inner side of the inner side surface in the axial direction of the rotary flange. 前記凹部が旋削加工により形成され、前記摺動面が研削加工されている事を特徴とする請求項１に記載のシール付車輪支持用軸受ユニット。   The bearing unit for supporting a wheel with a seal according to claim 1, wherein the concave portion is formed by turning, and the sliding surface is ground.
JP2011201381A 2011-09-15 2011-09-15 Bearing unit for supporting wheel with seal Withdrawn JP2013061048A (en)

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Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2017026061A (en) * 2015-07-23 2017-02-02 株式会社ジェイテクト Wheel bearing device, processing method of wheel bearing device and assembling method of wheel bearing device
EP3299649A1 (en) * 2016-09-26 2018-03-28 NTN-SNR Roulements Roller bearing provided with a sealing device
EP3276196A4 (en) * 2015-03-27 2019-01-02 NSK Ltd. Vehicle wheel bearing unit
WO2019110033A1 (en) * 2017-12-06 2019-06-13 Schaeffler Technologies AG & Co. KG Wheel bearing arrangement
WO2022264880A1 (en) 2021-06-14 2022-12-22 Ntn株式会社 Wheel bearing device

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3276196A4 (en) * 2015-03-27 2019-01-02 NSK Ltd. Vehicle wheel bearing unit
JP2017026061A (en) * 2015-07-23 2017-02-02 株式会社ジェイテクト Wheel bearing device, processing method of wheel bearing device and assembling method of wheel bearing device
EP3299649A1 (en) * 2016-09-26 2018-03-28 NTN-SNR Roulements Roller bearing provided with a sealing device
FR3056655A1 (en) * 2016-09-26 2018-03-30 Ntn-Snr Roulements BEARING BEARING EQUIPPED WITH A SEALING DEVICE
WO2019110033A1 (en) * 2017-12-06 2019-06-13 Schaeffler Technologies AG & Co. KG Wheel bearing arrangement
WO2022264880A1 (en) 2021-06-14 2022-12-22 Ntn株式会社 Wheel bearing device

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