WO2017014101A1 - Bearing with pulley - Google Patents

Bearing with pulley Download PDF

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Publication number
WO2017014101A1
WO2017014101A1 PCT/JP2016/070521 JP2016070521W WO2017014101A1 WO 2017014101 A1 WO2017014101 A1 WO 2017014101A1 JP 2016070521 W JP2016070521 W JP 2016070521W WO 2017014101 A1 WO2017014101 A1 WO 2017014101A1
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WO
WIPO (PCT)
Prior art keywords
bearing
pulley
dust cover
water
rolling bearing
Prior art date
Application number
PCT/JP2016/070521
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French (fr)
Japanese (ja)
Inventor
中尾　吾朗
麻理子 和泉
Original Assignee
Ntn株式会社
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Publication date
Application filed by Ntn株式会社 filed Critical Ntn株式会社
Priority to CN201680039489.0A priority Critical patent/CN107850122B/en
Publication of WO2017014101A1 publication Critical patent/WO2017014101A1/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
    • 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
    • F16C41/00—Other accessories, e.g. devices integrated in the bearing not relating to the bearing function as such
    • 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
    • F16H—GEARING
    • F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
    • F16H55/32—Friction members
    • F16H55/36—Pulleys
    • 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
    • F16C19/04—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly
    • F16C19/06—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly with a single row or balls

Definitions

  • This invention relates to a bearing with a pulley in an automobile engine.
  • belt movement is guided by idler pulleys, or tension pulleys are pressed against the belt by hydraulic auto tensioners to absorb belt tension fluctuations.
  • the tension is kept constant.
  • a bearing with a seal that prevents the entry of foreign matter into the bearing by a seal is generally used for a bearing that rotatably supports the pulley. Used for.
  • An object of the present invention is to provide a bearing with a pulley that can smoothly discharge water droplets that have entered the dust cover.
  • a rolling bearing with a seal a pulley having a boss portion in which the rolling bearing is incorporated in an inner peripheral portion, and dust covers provided on both sides of the rolling bearing are provided.
  • a configuration is adopted in which a water repellent process is applied to the inner surface of the dust cover facing the rolling bearing.
  • the gap amount is preferably 1.5 mm or less.
  • the wetting angle of the water droplet when it adheres to the water-repellent surface of the dust cover is smaller than necessary, the water droplet spreads outward and becomes an expanded wet state, and the adhesion of the water droplet to the dust cover increases. Therefore, the wetting angle is preferably 90 ° or more.
  • the wetting angle is the angle at which the water droplet surface forms the surface of the dust cover at the boundary line where the three layers contact when water droplets adhere to the dust cover and the surface of the dust cover is in contact with water droplets and gas. (Contact angle).
  • the bearing pulley surface facing the water repellent surface of the dust cover is subjected to water repellent treatment within a range not exceeding the wetting angle of the dust cover.
  • the water repellent finish is also applied to the bearing pulley surface, so that water droplets entering between the facing portions of the dust cover and the rolling bearing can be discharged more smoothly.
  • the water repellent treatment is applied to the inner side surface of the dust cover that covers the side surface of the rolling bearing, so that water droplets that have entered between the facing portions of the rolling bearing and the dust cover are caused by the rotation of the rolling bearing. Since it becomes easy to receive the influence of a centrifugal force, a water droplet can be discharged
  • the bearing with pulley includes a rolling bearing 10, a pulley 30 that is rotatably supported by the rolling bearing 10, and a pair of dust covers 40 and 41 provided on both sides of the rolling bearing 10. have.
  • a plurality of balls 15 are assembled between a raceway groove 12 formed on the inner diameter surface of the outer ring 11 and a raceway groove 14 formed on the outer diameter surface of the inner ring 13, and the balls 15 are held by a cage 16.
  • the bearing space formed between the outer ring 11 and the inner ring 13 is a ball bearing with a seal in which both ends of the bearing space are sealed with a pair of seals 17.
  • the seal 17 is supported at the outer peripheral portion by a seal mounting groove 18 formed at the end of the inner surface of the outer ring 11, and the inner peripheral portion has an inner portion as shown in FIG.
  • An inward lip 19a and an outward lip 19b are formed, and the inward lip 19a elastically contacts the inner wall 20a of the seal groove 20 formed at the end of the outer diameter surface of the inner ring 13, while the outward lip 19b
  • the space between the inner ring 13 and the inner ring 13 is sealed by elastic contact with a cylindrical land portion 21 formed outside the seal groove 20.
  • the rolling bearing 10 with a seal is not limited to a ball bearing.
  • a cylindrical roller bearing may be used.
  • each of the inward lip 19a and the outward lip 19b is elastically brought into contact with the corresponding surface, but only one of the inward lip 19a and the outward lip 19b is supported. You may make it make elastic contact with respect to.
  • the inner ring 13 of the roller bearing 10 with seal is supported in a non-rotating manner by screwing a bolt 22 inserted inside thereof into a screw hole 24 formed in the shaft end surface of the pulley shaft 23. .
  • the bolt 22 is provided with a large-diameter shaft portion 22b at the end portion of the screw shaft 22a, a flange 22c at the end portion of the large-diameter shaft portion 22b, and a head portion 22d at the end surface of the flange 22c.
  • the large-diameter shaft portion 22b is fitted to the inner ring 13 of the rolling bearing 10, and the screw shaft 22a is screwed into the screw hole 24 of the pulley shaft 23 and tightened, whereby the inner ring 13 is connected to the flange 22c and the pulley shaft.
  • the shaft end face 23 is clamped from both sides and fixed.
  • the pulley 30 has a belt guide wheel 31 on the outer peripheral portion, an annular flange 32 is formed on the inner diameter surface of the belt guide wheel 31, and a boss portion 33 is provided on the inner diameter portion of the annular flange 32.
  • an inward flange 34 is provided at one end of the boss portion 33, and an outer surface of the flange 34 is a tapered surface 35.
  • the pulley 30 is a metal molded product here, but may be a metal turning product or a resin molded product.
  • the belt guide wheel 31 is for a flat belt guide whose outer diameter surface is a cylindrical surface 31a, but is for a V belt guide having a plurality of V grooves formed on the outer diameter surface. There may be.
  • the pulley 30 is rotatably supported by press-fitting the outer ring 11 of the rolling bearing 10 inside the boss portion 33, and the pulley 30 and the rolling bearing 10 are brought into contact with the inward flange 34 against the inside side surface of the outer ring 11. Relative axial positioning is assumed. In the positioning state, the outer surface of the boss 33 forms the same surface as the outer side surface of the outer ring 11.
  • one of the outside dust covers 40 provided on the head 22 d side of the bolt 22 includes an inner ring portion 42 and its inner ring. It comprises an annular plate having an inclined part 43 provided continuously on the outer periphery of the part 42 and an outer ring part 44 provided continuously on the outer periphery of the inclined part 43.
  • the outer diameter of the outer ring part 44 is a pulley.
  • the outer diameter of the 30 boss portions 33 is the same.
  • the one dust cover 40 has an inner ring portion 42 fixed between the flange 22c of the bolt 22 and the inner ring 13 from both sides. At this time, the dust cover 40 is attached so that the inclined portion 43 bulges outward, and a gap 45 is provided between the outer ring portion 44 and the outer surface of the boss portion 33.
  • the gap amount in the axial direction of the gap 45 and [delta] 1 is a 1.5mm or less.
  • the other dust cover 41 on the screw shaft portion 22 a side of the bolt 22, that is, on the shaft end surface side of the pulley shaft 23, is connected to the inner ring portion 46 and the outer periphery of the inner ring portion 46. It comprises an annular plate having two stepped inclined portions 47 inclined in the same direction and an outer ring portion 48 connected to the outer periphery of the stepped inclined portion 47.
  • the diameter is the same as the outer diameter of the boss portion 33 of the pulley 30.
  • the other dust cover 41 is fixed with the inner ring portion 46 sandwiched from both sides by the inner ring 13 and the shaft end surface of the pulley shaft 23. At this time, the dust cover 41 is attached so that the stepped inclined portion 47 bulges outward, and a gap 49 is provided between the outer ring portion 48 and the outer surface of the boss portion 33.
  • the gap amount ⁇ 1 in the axial direction of the gap 49 has the same size as the gap amount ⁇ 1 in the axial direction of the gap 45 formed between the outer ring portion 44 of one dust cover 40 and the outer surface of the boss portion 33. ing.
  • Each of the pair of dust covers 40 and 41 is made of a press-formed product of a steel plate, and the inner side surface facing the side surface of the rolling bearing 10 is water-repellent processed, and as shown in FIGS. 2 and 3, the water-repellent layer 50 Is provided.
  • a primer is attached to the surface of the dust covers 40, 41, and a highly water repellent coating material such as Teflon is applied on the surface to a thickness of about 20-30 ⁇ m and baked at a high temperature.
  • a highly water repellent coating material such as Teflon
  • FIG. 4 shows a state in which water droplets A adhere to the surface of the water-repellent layer 50, and the wetting angle ⁇ of the water droplets A is 90 ° or more.
  • the wetting angle means that when the water droplet A adheres to the water repellent layer 50 and the surface of the water repellent layer 50 is in contact with the water droplet A and the gas, the water droplet surface repels at the boundary line where these three layers contact. A contact angle formed with the surface of the water layer 50.
  • the pulley-equipped bearing shown in the embodiment has the above-described structure, and the pulley-equipped bearing is used for moving guidance of an automobile accessory driving belt or for adjusting belt tension.
  • gaps 45, 49 formed between the dust covers 40, 41 and the boss portion 33 in the pulley 30 facing each other in the axial direction have an extremely small gap of 1.5 mm or less, the gap 45 , 49, almost no water drops enter the inside. However, as long as there are gaps 45 and 49, it is not possible to completely prevent water droplets from entering.
  • FIG. 2 shows a state in which water droplets A have entered between the dust cover 41 on the inside side and the seal 17 of the rolling bearing 10.
  • FIG. 3 shows a state in which the water droplet A has entered between the opposing surfaces of the dust cover 40 on the outside side and the boss portion 33 of the pulley 30.
  • FIG. 5 shows a state in which water droplets A have entered between the facing portions of the dust cover 40 and the boss portion 33 of the pulley 30 that have not been subjected to water repellent processing.
  • the water droplet A adheres to each of the inner surface of the dust cover 40 and the side surface of the boss portion 33.
  • each of the dust cover 40 and the pulley 30 is made of metal and has the same surface roughness, the adhesion force of the water droplet A to the inner surface of the dust cover 40 and the adhesion force of the water droplet A to the side surface of the boss portion 33 are substantially equal. It is said.
  • the pulley 30 is rotated by the movement of the belt guided by the belt guide wheel 31 on the outer periphery thereof, but the dust cover 40 is formed by the inner ring 13 of the rolling bearing 10 and the flange 22c of the bolt 22 as shown in FIG. Since it is clamped from both sides and fixed, the adhesion force of the water droplet A to the dust cover 40 becomes resistance, and the water droplet A is less affected by the centrifugal force, and the water droplet A cannot be discharged well.
  • the water droplet A since the water repellent layer 50 is provided on the inner surface of the dust cover 40, the water droplet A has a rounded surface on the dust cover 40 side and spreads on the surface on the boss portion 33 side. In an expanded wet state, the adhesion force of the water droplet A is large on the boss portion 33 side and small on the dust cover 40 side.
  • the seal 17 is made of rubber, and the dust cover 41 has a water repellent layer 50 on the inner surface. Therefore, the water droplet A is rounded on the surface on the dust cover 41 side, and is in an expanded wet state with a spread on the surface on the boss portion 33 side, and the adhesion force of the water droplet A is large on the seal 17 side, It becomes small on the dust cover 41 side.
  • the wetting angle ⁇ of the water droplet A with the water droplet A adhering to the surface of the water repellent layer 50 is set to 90 ° or more, the water droplet A that has entered can be discharged more effectively. it can.
  • the bearing pulley surface (including the outer ring 11, the seal 17, and the seal groove 20) facing the water repellent surface of the dust covers 40, 41 is subjected to water repellent processing within a range not exceeding the wetting angle of the dust covers 40, 41. You may do it.
  • the water droplet A that has entered can be more effectively discharged by applying water repellent treatment to the bearing pulley surface.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Sealing Of Bearings (AREA)
  • Pulleys (AREA)
  • Rolling Contact Bearings (AREA)
  • Sealing Using Fluids, Sealing Without Contact, And Removal Of Oil (AREA)
  • Sealing Devices (AREA)

Abstract

The present invention is a bearing with a pulley configured so that water droplets (A) are smoothly discharged by: providing dust covers (40, 41) on both sides of a roller bearing (10) with seals that supports a pulley (30) so as to roll freely; and applying a water repellent finish on the respective inner surfaces of said dust covers (40, 41) to reduce the adhesion of water droplets (A), which infiltrate the dust covers (40, 41), to the dust covers (40, 41) and make the water droplets more susceptible to the effects of centrifugal force resulting from rotation of the roller bearing (10).

Description

プーリ付き軸受Bearing with pulley
　この発明は、自動車エンジンにおけるプーリ付き軸受に関する。 This invention relates to a bearing with a pulley in an automobile engine.
　オルタネータやコンプレッサ等の自動車補機を駆動するベルト伝動装置においては、アイドラプーリによってベルトの移動を案内し、あるいは、油圧式オートテンショナによりテンションプーリをベルトに押し付けてベルトの張力変動を吸収し、ベルト張力を一定に保つようにしている。 In belt transmissions that drive automotive auxiliary equipment such as alternators and compressors, belt movement is guided by idler pulleys, or tension pulleys are pressed against the belt by hydraulic auto tensioners to absorb belt tension fluctuations. The tension is kept constant.
　上記のようなアイドラプーリやテンションプーリは、外部に露出する組み付けであるため、そのプーリを回転自在に支持する軸受には、シールによって軸受内部への異物の侵入を防止するシール付き軸受が一般的に使用される。 Since idler pulleys and tension pulleys such as those described above are assembled to be exposed to the outside, a bearing with a seal that prevents the entry of foreign matter into the bearing by a seal is generally used for a bearing that rotatably supports the pulley. Used for.
　しかし、シール付き軸受に組み込まれたシールのみで泥水などの異物の軸受内への侵入を防止する場合、異物との接触によってシールが損傷し易く、耐久性に問題があるため、シール付き軸受の両側にダストカバーを設けてシールの損傷を防止し、軸受のシール性の向上を図ることが行われている（下記特許文献１、２参照）。 However, if the intrusion of foreign matter such as muddy water into the bearing with only the seal incorporated in the sealed bearing is likely to be damaged due to contact with the foreign matter, there is a problem with durability. Dust covers are provided on both sides to prevent seal damage and improve the sealability of the bearing (see Patent Documents 1 and 2 below).
特開２００９－２１６１３８号公報JP 2009-216138 A 特開２００９－１７４６８３号公報JP 2009-174683 A
　ところで、特許文献１および２に記載されたプーリ付き軸受においては、シール付き軸受とダストカバーとの対向部間に形成された間隙が小さく、また、特許文献２に記載されたプーリ付き軸受においては、プーリの側面に環状の突条を設け、その突条によってシール付き軸受とダストカバーとの対向部間に形成された間隙を覆うようにしているため、上記間隙からダストカバー内に水滴が浸入することは少ないが、万一浸入すると、スムーズに排出することができない。 By the way, in the bearing with pulley described in Patent Documents 1 and 2, the gap formed between the opposed portions of the bearing with seal and the dust cover is small. In the bearing with pulley described in Patent Document 2, An annular ridge is provided on the side of the pulley, and the ridge covers the gap formed between the opposed portion of the bearing with seal and the dust cover, so that water droplets enter the dust cover from the gap. However, if it enters, it cannot be discharged smoothly.
　すなわち、シール付き軸受とダストカバーとの対向部間に形成された間隙内に水滴が浸入した場合、その水滴はシール付き軸受の側面とダストカバーの内側面の両方に付着する。このとき、ダストカバーは軸受の内輪に支持されて回転することがなく、そのダストカバー側の水滴の付着力が抵抗となって遠心力の影響を受けることが少なくなり、水滴を良好に排出することができない。 That is, when water droplets enter the gap formed between the opposed portions of the sealed bearing and the dust cover, the water droplets adhere to both the side surface of the sealed bearing and the inner surface of the dust cover. At this time, the dust cover is supported by the inner ring of the bearing and does not rotate, and the adhesion force of the water droplet on the dust cover side becomes a resistance and is less affected by the centrifugal force, and the water droplet is discharged well. I can't.
　近年では、従来では考慮されていなかった悪路走行等の条件が増え、ダストカバーでの対策だけでは、軸受内部に異物の侵入が認められており、その結果としてプーリ付き軸受の耐水要求が高まってきている。 In recent years, conditions such as driving on rough roads that have not been considered in the past have increased, and foreign matter intrusion has been recognized inside the bearing only by measures with the dust cover, and as a result, the water resistance requirement of bearings with pulleys has increased. It is coming.
　この発明の課題は、ダストカバー内に浸入した水滴を円滑に排出することができるようにしたプーリ付き軸受を提供することである。 An object of the present invention is to provide a bearing with a pulley that can smoothly discharge water droplets that have entered the dust cover.
　上記の課題を解決するため、この発明においては、シール付き転がり軸受と、その転がり軸受が組み込まれたボス部を内周部に有するプーリと、前記転がり軸受の両側に設けられたダストカバーとを有してなり、前記ダストカバーによって前記転がり軸受の側面を覆うようにしたプーリ付き軸受において、前記ダストカバーの前記転がり軸受と対向する内側面に撥水加工を施した構成を採用したのである。 In order to solve the above problems, in the present invention, a rolling bearing with a seal, a pulley having a boss portion in which the rolling bearing is incorporated in an inner peripheral portion, and dust covers provided on both sides of the rolling bearing are provided. In the bearing with pulley, which covers the side surface of the rolling bearing with the dust cover, a configuration is adopted in which a water repellent process is applied to the inner surface of the dust cover facing the rolling bearing.
　上記のように、ダストカバーの内側面に撥水加工を施すことにより、ダストカバーと転がり軸受の対向部間に万一水滴が浸入した場合、その水滴の付着力は転がり軸受側で大きく、ダストカバー側で小さいものとなり、転がり軸受の回転により、その転がり軸受と共に水滴が回転する。このため、水滴は負荷される遠心力により径方向外方に向けて移動して外部にスムーズに排出されることになる。 As described above, by applying water-repellent treatment to the inner surface of the dust cover, in the unlikely event that a water droplet enters between the opposing portions of the dust cover and the rolling bearing, the adhesion force of the water droplet is large on the rolling bearing side, It becomes small on the cover side, and water droplets rotate together with the rolling bearing by the rotation of the rolling bearing. For this reason, the water droplet moves outward in the radial direction by the applied centrifugal force and is smoothly discharged to the outside.
　この発明に係るプーリ付き軸受において、ダストカバーの外周部に形成された外環部と転がり軸受の外輪側面との対向部間に形成される間隙の軸方向の間隙量が大きくなり過ぎると、異物が侵入し易くなるため、上記間隙量は１．５ｍｍ以下とするのがよい。 In the bearing with pulley according to the present invention, if the axial gap amount of the gap formed between the outer ring portion formed on the outer peripheral portion of the dust cover and the outer ring side surface of the rolling bearing is excessively large, Therefore, the gap amount is preferably 1.5 mm or less.
　また、ダストカバーの撥水加工面に水滴が付着した際の水滴の濡れ角度が必要以上に小さい場合は、水滴が外方に拡がりをもって拡張濡れ状態となり、ダストカバーに対する水滴の付着力が大きくなって遠心力の影響を受けることが少なくなるため、上記濡れ角度は９０°以上とすることが好ましい。 In addition, if the wetting angle of the water droplet when it adheres to the water-repellent surface of the dust cover is smaller than necessary, the water droplet spreads outward and becomes an expanded wet state, and the adhesion of the water droplet to the dust cover increases. Therefore, the wetting angle is preferably 90 ° or more.
　ここで、濡れ角度とは、ダストカバーに水滴が付着し、ダストカバーの表面が水滴および気体と接触しているとき、この３層が接触する境界線において水滴面がダストカバーの表面と成す角度（接触角）をいう。 Here, the wetting angle is the angle at which the water droplet surface forms the surface of the dust cover at the boundary line where the three layers contact when water droplets adhere to the dust cover and the surface of the dust cover is in contact with water droplets and gas. (Contact angle).
　この発明に係るプーリ付き軸受において、ダストカバーの撥水加工面と対向する軸受プーリ面にダストカバーの濡れ角度を超えない範囲で撥水加工を施すのがよい。このように、軸受プーリ面にも撥水加工を施すことによって、ダストカバーと転がり軸受の対向部間に浸入する水滴をより円滑に排出することができる。 In the bearing with pulley according to the present invention, it is preferable that the bearing pulley surface facing the water repellent surface of the dust cover is subjected to water repellent treatment within a range not exceeding the wetting angle of the dust cover. As described above, the water repellent finish is also applied to the bearing pulley surface, so that water droplets entering between the facing portions of the dust cover and the rolling bearing can be discharged more smoothly.
　この発明においては、上記のように、転がり軸受の側面を覆うダストカバーの内側面に撥水加工を施したことにより、転がり軸受とダストカバーの対向部間に浸入した水滴は転がり軸受の回転による遠心力の影響を受け易くなるため、水滴を円滑に排出することができる。 In the present invention, as described above, the water repellent treatment is applied to the inner side surface of the dust cover that covers the side surface of the rolling bearing, so that water droplets that have entered between the facing portions of the rolling bearing and the dust cover are caused by the rotation of the rolling bearing. Since it becomes easy to receive the influence of a centrifugal force, a water droplet can be discharged | emitted smoothly.
この発明の実施形態に係るプーリ付き軸受の縦断面図The longitudinal cross-sectional view of the bearing with a pulley which concerns on embodiment of this invention 図１のインサイド側ダストカバーと転がり軸受の一部分を拡大して示す断面図Sectional drawing which expands and shows a part of inside dust cover and rolling bearing of FIG. 図１のアウトサイド側ダストカバーとプーリのボス部の一部分を拡大して示す断面図Sectional drawing which expands and shows a part of boss | hub part of the outside dust cover and pulley of FIG. ダストカバーに付着した水滴の濡れ角度を示す図Diagram showing the wetting angle of water droplets adhering to the dust cover 従来のプーリ付き軸受に対する水滴の付着状態を示す断面図Sectional view showing the state of water droplet adhesion to a conventional bearing with pulley
　以下、この発明の実施の形態を図面に基づいて説明する。図１に示すように、プーリ付き軸受は、転がり軸受１０と、その転がり軸受１０によって回転自在に支持されたプーリ３０と、上記転がり軸受１０の両側に設けられた一対のダストカバー４０、４１とを有している。 Hereinafter, embodiments of the present invention will be described with reference to the drawings. As shown in FIG. 1, the bearing with pulley includes a rolling bearing 10, a pulley 30 that is rotatably supported by the rolling bearing 10, and a pair of dust covers 40 and 41 provided on both sides of the rolling bearing 10. have.
　転がり軸受１０は、外輪１１の内径面に形成された軌道溝１２と、内輪１３の外径面に形成された軌道溝１４間に複数のボール１５を組込み、そのボール１５を保持器１６で保持し、上記外輪１１と内輪１３の対向部間に形成された軸受空間の両端開口を一対のシール１７で密閉したシール付きの玉軸受からなる。 In the rolling bearing 10, a plurality of balls 15 are assembled between a raceway groove 12 formed on the inner diameter surface of the outer ring 11 and a raceway groove 14 formed on the outer diameter surface of the inner ring 13, and the balls 15 are held by a cage 16. The bearing space formed between the outer ring 11 and the inner ring 13 is a ball bearing with a seal in which both ends of the bearing space are sealed with a pair of seals 17.
　ここで、シール１７は、図３に示すように、外輪１１の内径面端部に形成されたシール取付溝１８で外周部が支持され、内周部には、図２に示すように、内向きリップ１９ａと外向きリップ１９ｂが形成され、上記内向きリップ１９ａが内輪１３の外径面の端部に形成されたシール溝２０の内側壁２０ａに弾性接触し、一方、外向きリップ１９ｂがシール溝２０の外側に形成された円筒形のランド部２１に弾性接触して、内輪１３との間を密閉している。 Here, as shown in FIG. 3, the seal 17 is supported at the outer peripheral portion by a seal mounting groove 18 formed at the end of the inner surface of the outer ring 11, and the inner peripheral portion has an inner portion as shown in FIG. An inward lip 19a and an outward lip 19b are formed, and the inward lip 19a elastically contacts the inner wall 20a of the seal groove 20 formed at the end of the outer diameter surface of the inner ring 13, while the outward lip 19b The space between the inner ring 13 and the inner ring 13 is sealed by elastic contact with a cylindrical land portion 21 formed outside the seal groove 20.
　なお、シール付き転がり軸受１０は、玉軸受に限定されない。例えば、円筒ころ軸受であってもよい。 In addition, the rolling bearing 10 with a seal is not limited to a ball bearing. For example, a cylindrical roller bearing may be used.
　また、図２では、内向きリップ１９ａおよび外向きリップ１９ｂのそれぞれを対応する面に対して弾性接触させるようにしたが、内向きリップ１９ａおよび外向きリップ１９ｂのいずれか一方のみを対応する面に対して弾性接触させるようにしてもよい。 In FIG. 2, each of the inward lip 19a and the outward lip 19b is elastically brought into contact with the corresponding surface, but only one of the inward lip 19a and the outward lip 19b is supported. You may make it make elastic contact with respect to.
　図１に示すように、シール付き転がり軸受１０の内輪１３は、その内側に挿入されたボルト２２をプーリ軸２３の軸端面に形成されたねじ孔２４にねじ込むことによって非回転の支持とされる。 As shown in FIG. 1, the inner ring 13 of the roller bearing 10 with seal is supported in a non-rotating manner by screwing a bolt 22 inserted inside thereof into a screw hole 24 formed in the shaft end surface of the pulley shaft 23. .
　ここで、ボルト２２は、ねじ軸２２ａの端部に大径軸部２２ｂが設けられ、その大径軸部２２ｂの端部にフランジ２２ｃと、そのフランジ２２ｃの端面に頭部２２ｄが設けられた構成とされており、上記大径軸部２２ｂが転がり軸受１０の内輪１３に嵌合され、プーリ軸２３のねじ孔２４にねじ軸２２ａをねじ込んで締め付けることによって、内輪１３がフランジ２２ｃとプーリ軸２３の軸端面で両側から挟持されて固定とされる。 Here, the bolt 22 is provided with a large-diameter shaft portion 22b at the end portion of the screw shaft 22a, a flange 22c at the end portion of the large-diameter shaft portion 22b, and a head portion 22d at the end surface of the flange 22c. The large-diameter shaft portion 22b is fitted to the inner ring 13 of the rolling bearing 10, and the screw shaft 22a is screwed into the screw hole 24 of the pulley shaft 23 and tightened, whereby the inner ring 13 is connected to the flange 22c and the pulley shaft. The shaft end face 23 is clamped from both sides and fixed.
　プーリ３０は、外周部にベルト案内輪３１を有し、そのベルト案内輪３１の内径面に環状フランジ３２が形成され、その環状フランジ３２の内径部にボス部３３が設けられている。また、ボス部３３の一方の端部には内向きフランジ３４が設けられ、そのフランジ３４の外側面はテーパ面３５とされている。 The pulley 30 has a belt guide wheel 31 on the outer peripheral portion, an annular flange 32 is formed on the inner diameter surface of the belt guide wheel 31, and a boss portion 33 is provided on the inner diameter portion of the annular flange 32. In addition, an inward flange 34 is provided at one end of the boss portion 33, and an outer surface of the flange 34 is a tapered surface 35.
　なお、プーリ３０として、ここでは、金属の成形品としているが、金属の旋削加工品であってもよく、あるいは、樹脂の成形品であってもよい。 The pulley 30 is a metal molded product here, but may be a metal turning product or a resin molded product.
　また、ベルト案内輪３１として、ここでは、外径面が円筒面３１ａからなる平ベルト案内用のものを示したが、外径面に複数のＶ溝が形成されたＶベルト案内用のものであってもよい。 Further, here, the belt guide wheel 31 is for a flat belt guide whose outer diameter surface is a cylindrical surface 31a, but is for a V belt guide having a plurality of V grooves formed on the outer diameter surface. There may be.
　プーリ３０は、ボス部３３の内側に転がり軸受１０の外輪１１が圧入されて回転自在に支持され、その外輪１１のインサイド側の側面に対する内向きフランジ３４の当接によってプーリ３０と転がり軸受１０の相対的な軸方向の位置決めとされている。その位置決め状態においてボス部３３の外側面は外輪１１のアウトサイド側の側面と同一面を形成している。 The pulley 30 is rotatably supported by press-fitting the outer ring 11 of the rolling bearing 10 inside the boss portion 33, and the pulley 30 and the rolling bearing 10 are brought into contact with the inward flange 34 against the inside side surface of the outer ring 11. Relative axial positioning is assumed. In the positioning state, the outer surface of the boss 33 forms the same surface as the outer side surface of the outer ring 11.
　転がり軸受１０の両側に設けられた一対のダストカバー４０、４１のうち、ボルト２２の頭部２２ｄ側に設けられたアウトサイド側の一方のダストカバー４０は、内環部４２と、その内環部４２の外周に連設された傾斜部４３と、その傾斜部４３の外周に連設された外環部４４とを有してなる環状板からなり、上記外環部４４の外径はプーリ３０のボス部３３の外径と同径とされている。 Of the pair of dust covers 40, 41 provided on both sides of the rolling bearing 10, one of the outside dust covers 40 provided on the head 22 d side of the bolt 22 includes an inner ring portion 42 and its inner ring. It comprises an annular plate having an inclined part 43 provided continuously on the outer periphery of the part 42 and an outer ring part 44 provided continuously on the outer periphery of the inclined part 43. The outer diameter of the outer ring part 44 is a pulley. The outer diameter of the 30 boss portions 33 is the same.
　上記一方のダストカバー４０は内環部４２がボルト２２のフランジ２２ｃと内輪１３とで両側から挟持されて固定とされている。このとき、ダストカバー４０は、傾斜部４３が外側方に膨出する取り付けとされて、外環部４４とボス部３３の外側面間に間隙４５が設けられている。上記間隙４５の軸方向の間隙量をδ１とすると、そのδ１は１．５ｍｍ以下とされている。 The one dust cover 40 has an inner ring portion 42 fixed between the flange 22c of the bolt 22 and the inner ring 13 from both sides. At this time, the dust cover 40 is attached so that the inclined portion 43 bulges outward, and a gap 45 is provided between the outer ring portion 44 and the outer surface of the boss portion 33. When the gap amount in the axial direction of the gap 45 and [delta] 1, the [delta] 1 is a 1.5mm or less.
　ボルト２２のねじ軸部２２ａ側、すなわち、プーリ軸２３の軸端面側に設けられたインサイド側の他方のダストカバー４１は、内環部４６と、その内環部４６の外周に連設された２段の同方向に傾斜する段付き傾斜部４７と、その段付き傾斜部４７の外周に連設された外環部４８とを有してなる環状板からなり、上記外環部４８の外径はプーリ３０のボス部３３の外径と同径とされている。 The other dust cover 41 on the screw shaft portion 22 a side of the bolt 22, that is, on the shaft end surface side of the pulley shaft 23, is connected to the inner ring portion 46 and the outer periphery of the inner ring portion 46. It comprises an annular plate having two stepped inclined portions 47 inclined in the same direction and an outer ring portion 48 connected to the outer periphery of the stepped inclined portion 47. The diameter is the same as the outer diameter of the boss portion 33 of the pulley 30.
　上記他方のダストカバー４１は、内環部４６が内輪１３とプーリ軸２３の軸端面とで両側から挟持されて固定とされている。このとき、ダストカバー４１は、段付き傾斜部４７が外側方に膨出する取り付けとされて、外環部４８とボス部３３の外側面間に間隙４９が設けられている。上記間隙４９の軸方向の間隙量δ１は、一方のダストカバー４０の外環部４４とボス部３３の外側面間に形成された間隙４５の軸方向の間隙量δ１と同じ大きさとされている。 The other dust cover 41 is fixed with the inner ring portion 46 sandwiched from both sides by the inner ring 13 and the shaft end surface of the pulley shaft 23. At this time, the dust cover 41 is attached so that the stepped inclined portion 47 bulges outward, and a gap 49 is provided between the outer ring portion 48 and the outer surface of the boss portion 33. The gap amount δ 1 in the axial direction of the gap 49 has the same size as the gap amount δ 1 in the axial direction of the gap 45 formed between the outer ring portion 44 of one dust cover 40 and the outer surface of the boss portion 33. ing.
　一対のダストカバー４０、４１のそれぞれは、鋼板のプレス成形品からなり、転がり軸受１０の側面と対向する内側面は撥水加工されて、図２および図３に示すように、撥水層５０が設けられている。 Each of the pair of dust covers 40 and 41 is made of a press-formed product of a steel plate, and the inner side surface facing the side surface of the rolling bearing 10 is water-repellent processed, and as shown in FIGS. 2 and 3, the water-repellent layer 50 Is provided.
　撥水加工として、ここでは、ダストカバー４０、４１の表面にプライマを着け、その上にテフロン等の撥水性の高いコーティング材を厚さ２０～３０μｍ程度に塗布して高温で焼付けるようにしているが、これに限定されるものではない。 Here, as a water repellent treatment, a primer is attached to the surface of the dust covers 40, 41, and a highly water repellent coating material such as Teflon is applied on the surface to a thickness of about 20-30 μm and baked at a high temperature. However, it is not limited to this.
　ここで、図４は、撥水層５０の表面に水滴Ａが付着した状態を示し、その水滴Ａの濡れ角度αは９０°以上とされている。ここで、濡れ角度とは、撥水層５０に水滴Ａが付着し、撥水層５０の表面が水滴Ａおよび気体と接触しているとき、この３層が接触する境界線において水滴面が撥水層５０の表面と成す接触角をいう。 Here, FIG. 4 shows a state in which water droplets A adhere to the surface of the water-repellent layer 50, and the wetting angle α of the water droplets A is 90 ° or more. Here, the wetting angle means that when the water droplet A adheres to the water repellent layer 50 and the surface of the water repellent layer 50 is in contact with the water droplet A and the gas, the water droplet surface repels at the boundary line where these three layers contact. A contact angle formed with the surface of the water layer 50.
　実施の形態で示すプーリ付き軸受は上記の構造からなり、そのプーリ付き軸受は、自動車補機駆動用ベルトの移動案内用として、あるいは、ベルトの張力調整用として用いられる。 The pulley-equipped bearing shown in the embodiment has the above-described structure, and the pulley-equipped bearing is used for moving guidance of an automobile accessory driving belt or for adjusting belt tension.
　上記のような使用では、外部に露出する取り付けであるため、悪路での走行時、飛散する泥水がプーリ３０内に侵入してくる場合が多い。このとき、プーリ３０を回転自在に支持する転がり軸受１０の両側にはダストカバー４０、４１が設けられているため、そのダストカバー４０、４１によって転がり軸受１０のシール１７に対する泥水等の異物の衝突を避けることができ、シール１７の損傷を防止することができる。 In the use as described above, since the mounting is exposed to the outside, the scattered muddy water often enters the pulley 30 when traveling on a rough road. At this time, since dust covers 40 and 41 are provided on both sides of the rolling bearing 10 that rotatably supports the pulley 30, the dust covers 40 and 41 collide foreign matter such as muddy water against the seal 17 of the rolling bearing 10. Can be avoided, and damage to the seal 17 can be prevented.
　また、ダストカバー４０、４１とプーリ３０におけるボス部３３の対向面間に形成された間隙４５、４９の軸方向の間隙量は１．５ｍｍ以下とされた極めて小さなものであるため、その間隙４５、４９から内部に水滴が浸入することは殆どない。しかし、間隙４５、４９がある以上、水滴の浸入を完全に防止することはできない。 Further, since the gaps 45, 49 formed between the dust covers 40, 41 and the boss portion 33 in the pulley 30 facing each other in the axial direction have an extremely small gap of 1.5 mm or less, the gap 45 , 49, almost no water drops enter the inside. However, as long as there are gaps 45 and 49, it is not possible to completely prevent water droplets from entering.
　図２は、インサイド側のダストカバー４１と転がり軸受１０のシール１７間に水滴Ａが浸入した状態を示す。また、図３は、アウトサイド側のダストカバー４０とプーリ３０のボス部３３の対向面間に水滴Ａが浸入した状態を示す。 FIG. 2 shows a state in which water droplets A have entered between the dust cover 41 on the inside side and the seal 17 of the rolling bearing 10. FIG. 3 shows a state in which the water droplet A has entered between the opposing surfaces of the dust cover 40 on the outside side and the boss portion 33 of the pulley 30.
　ここで、ダストカバー４０、４１のそれぞれの内側面は撥水加工が施されて撥水層５０が設けられているため、水滴Ａをスムーズに排出することができる。その水滴Ａの排出について以下に説明する。 Here, since each of the inner surfaces of the dust covers 40 and 41 is subjected to water-repellent finishing and the water-repellent layer 50 is provided, the water droplets A can be discharged smoothly. The discharge of the water droplet A will be described below.
　図５は、撥水加工が施されていないダストカバー４０とプーリ３０のボス部３３の対向部間に水滴Ａが浸入した状態を示す。図５に示すように、ダストカバー４０の内側面に撥水加工が施されていないと、水滴Ａはダストカバー４０の内側面とボス部３３の側面のそれぞれに付着する。ダストカバー４０およびプーリ３０のそれぞれが金属で形成されて表面粗さが同じである場合、ダストカバー４０の内側面に対する水滴Ａの付着力とボス部３３の側面に対する水滴Ａの付着力は略同等とされる。 FIG. 5 shows a state in which water droplets A have entered between the facing portions of the dust cover 40 and the boss portion 33 of the pulley 30 that have not been subjected to water repellent processing. As shown in FIG. 5, when the inner surface of the dust cover 40 is not subjected to water repellent processing, the water droplet A adheres to each of the inner surface of the dust cover 40 and the side surface of the boss portion 33. When each of the dust cover 40 and the pulley 30 is made of metal and has the same surface roughness, the adhesion force of the water droplet A to the inner surface of the dust cover 40 and the adhesion force of the water droplet A to the side surface of the boss portion 33 are substantially equal. It is said.
　ここで、プーリ３０は、その外周のベルト案内輪３１で案内されるベルトの移動によって回転するが、ダストカバー４０は図１に示すように、転がり軸受１０の内輪１３とボルト２２のフランジ２２ｃで両側から挟持されて固定されているため、ダストカバー４０に対する水滴Ａの付着力が抵抗となって、水滴Ａは遠心力の影響を受けることが少なく、水滴Ａを良好に排出することができない。 Here, the pulley 30 is rotated by the movement of the belt guided by the belt guide wheel 31 on the outer periphery thereof, but the dust cover 40 is formed by the inner ring 13 of the rolling bearing 10 and the flange 22c of the bolt 22 as shown in FIG. Since it is clamped from both sides and fixed, the adhesion force of the water droplet A to the dust cover 40 becomes resistance, and the water droplet A is less affected by the centrifugal force, and the water droplet A cannot be discharged well.
　しかし、実施の形態においては、ダストカバー４０の内側面には撥水層５０を設けているため、水滴Ａはダストカバー４０側で表面に丸みを帯び、ボス部３３側で表面に拡がりを持つ拡張濡れ状態となって、水滴Ａの付着力がボス部３３側で大きく、ダストカバー４０側で小さいものとなる。 However, in the embodiment, since the water repellent layer 50 is provided on the inner surface of the dust cover 40, the water droplet A has a rounded surface on the dust cover 40 side and spreads on the surface on the boss portion 33 side. In an expanded wet state, the adhesion force of the water droplet A is large on the boss portion 33 side and small on the dust cover 40 side.
　このため、プーリ３０が回転することにより、そのプーリ３０のボス部３３と共に水滴Ａが回転する。このため、水滴Ａは負荷される遠心力により、図３の矢印で示すように、径方向外方に向けて移動して外部にスムーズに排出されることになる。 Therefore, when the pulley 30 is rotated, the water droplet A is rotated together with the boss portion 33 of the pulley 30. For this reason, the water droplet A is moved outward in the radial direction and smoothly discharged to the outside as indicated by the arrow in FIG. 3 due to the centrifugal force applied.
　一方、図２に示すように、インサイド側のダストカバー４１と転がり軸受１０のシール１７間に水滴Ａが浸入した場合、シール１７はゴム製であり、ダストカバー４１は内側面に撥水層５０が設けられているため、水滴Ａはダストカバー４１側で表面に丸みを帯び、ボス部３３側で表面に拡がりを持つ拡張濡れ状態となって、水滴Ａの付着力はシール１７側で大きく、ダストカバー４１側で小さいものとなる。 On the other hand, as shown in FIG. 2, when the water droplet A enters between the dust cover 41 on the inside side and the seal 17 of the rolling bearing 10, the seal 17 is made of rubber, and the dust cover 41 has a water repellent layer 50 on the inner surface. Therefore, the water droplet A is rounded on the surface on the dust cover 41 side, and is in an expanded wet state with a spread on the surface on the boss portion 33 side, and the adhesion force of the water droplet A is large on the seal 17 side, It becomes small on the dust cover 41 side.
　このため、プーリ３０が回転することにより、転がり軸受１０の外輪１１と共にシール１７が回転し、そのシール１７と共に水滴Ａが回転する。このため、水滴Ａは負荷される遠心力により、図２の矢印で示すように、径方向外方に向けて移動して外部にスムーズに排出されることになる。 Therefore, when the pulley 30 is rotated, the seal 17 is rotated together with the outer ring 11 of the rolling bearing 10, and the water droplet A is rotated together with the seal 17. For this reason, the water droplet A is moved outward in the radial direction and smoothly discharged to the outside by the applied centrifugal force as shown by the arrow in FIG.
　図４に示すように、撥水層５０の表面に水滴Ａが付着した状態での水滴Ａの濡れ角度αを９０°以上とすることにより、浸入した水滴Ａをより効果的に排出することができる。 As shown in FIG. 4, when the wetting angle α of the water droplet A with the water droplet A adhering to the surface of the water repellent layer 50 is set to 90 ° or more, the water droplet A that has entered can be discharged more effectively. it can.
　なお、ダストカバー４０、４１の撥水加工面と対向する軸受プーリ面（外輪１１、シール１７、シール溝２０を含む）にダストカバー４０，４１の濡れ角度を超えない範囲で撥水加工を施すようにしてもよい。軸受プーリ面にも撥水加工を施すことによって浸入した水滴Ａをより効果的に排出することができる。 The bearing pulley surface (including the outer ring 11, the seal 17, and the seal groove 20) facing the water repellent surface of the dust covers 40, 41 is subjected to water repellent processing within a range not exceeding the wetting angle of the dust covers 40, 41. You may do it. The water droplet A that has entered can be more effectively discharged by applying water repellent treatment to the bearing pulley surface.
１０　転がり軸受
３０　プーリ
３３　ボス部
４０　ダストカバー
４１　ダストカバー
４４　外環部
４８　外環部
５０　撥水層 DESCRIPTION OF SYMBOLS 10 Rolling bearing 30 Pulley 33 Boss part 40 Dust cover 41 Dust cover 44 Outer ring part 48 Outer ring part 50 Water repellent layer

Claims (4)

  1. 　シール付き転がり軸受（１０）と、その転がり軸受（１０）が組み込まれたボス部（３３）を内周部に有するプーリ（３０）と、前記転がり軸受（１０）の両側に設けられたダストカバー（４０、４１）とを有してなり、前記ダストカバー（４０、４１）によって前記転がり軸受（１０）の側面を覆うようにしたプーリ付き軸受において、
    　前記ダストカバー（４０、４１）の前記転がり軸受と対向する内側面に撥水加工を施したことを特徴とするプーリ付き軸受。     A rolling bearing (10) with a seal, a pulley (30) having a boss part (33) in which the rolling bearing (10) is incorporated, and a dust cover provided on both sides of the rolling bearing (10) (40, 41), and a pulley-equipped bearing that covers the side surface of the rolling bearing (10) with the dust cover (40, 41).
    A bearing with a pulley, characterized in that a water repellent finish is applied to an inner surface of the dust cover (40, 41) facing the rolling bearing.
  2. 　前記ダストカバー（４０、４１）の外周部に形成された外環部（４４、４８）と前記転がり軸受（１０）の外輪側面との対向部間に形成される間隙（４５、４９）の軸方向の間隙量を１．５ｍｍ以下とした請求項１に記載のプーリ付き軸受。 Shafts of gaps (45, 49) formed between the outer ring portions (44, 48) formed on the outer peripheral portion of the dust cover (40, 41) and the facing portions of the outer ring side surface of the rolling bearing (10). The bearing with a pulley according to claim 1, wherein a gap amount in a direction is 1.5 mm or less.
  3. 　前記ダストカバー（４０、４１）の撥水加工面に水滴が付着した際の水滴の濡れ角度を９０°以上とした請求項１又は２に記載のプーリ付き軸受。 The bearing with a pulley according to claim 1 or 2, wherein a wetting angle of the water droplet when the water droplet adheres to the water repellent surface of the dust cover (40, 41) is 90 ° or more.
  4. 　前記ダストカバー（４０、４１）の撥水加工面と対向する軸受プーリ面にダストカバー（４０、４１）の濡れ角度を超えない範囲で撥水加工を施した請求項１乃至３のいずれか１項に記載のプーリ付き軸受。 The water repellent finish is applied to the bearing pulley surface facing the water repellent finish surface of the dust cover (40, 41) within a range not exceeding the wetting angle of the dust cover (40, 41). The bearing with a pulley as described in the item.
PCT/JP2016/070521 2015-07-22 2016-07-12 Bearing with pulley WO2017014101A1 (en)

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JP2002303330A (en) * 2001-02-05 2002-10-18 Nsk Ltd Rolling bearing
JP2008256197A (en) * 2007-03-14 2008-10-23 Nsk Ltd Rolling bearing and its manufacturing method
JP2009074480A (en) * 2007-09-21 2009-04-09 Jtekt Corp Water pump
JP2009174683A (en) * 2008-01-28 2009-08-06 Ntn Corp Bearing with resin pulley
JP2011117475A (en) * 2009-12-01 2011-06-16 Ntn Corp Bearing device for wheel
JP2012167809A (en) * 2011-01-27 2012-09-06 Nsk Ltd Rolling bearing
JP2012167818A (en) * 2012-04-18 2012-09-06 Mitsubishi Electric Corp Electric motor
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